Inertial igniters for low-G and long-duration firing acceleration munitions and the like

Abstract

An inertial mechanism including a member rotatable about an axis between activatable and activated positions, in the activatable position a first center of mass of the member is offset from the axis in a direction perpendicular to a direction of acceleration, the member having a surface; and another member rotatable about an axis between rest and activated positions, the rest position being where the second member cannot be moved into its activated position from an acceleration event, the other member also having a surface, the surfaces engage with each other when the member moves to its activated position to move the other member from its rest position to its activatable position, which is also where a center of mass of the other member is offset from its axis in the direction perpendicular to the direction of the acceleration.

Description

BACKGROUND

1. Field of the Invention

The present disclosure relates generally to mechanical inertial igniters, and more particularly to compact, reliable mechanical inertial igniters for activating reserve batteries and the like in munitions with relatively low-G and long duration firing acceleration.

2. Prior Art

Reserve batteries of the electrochemical type are well known in the art for a variety of uses where storage time before use is extremely long. Reserve batteries are in use in applications such as batteries for gun-fired munitions including guided and smart, mortars, fusing mines, missiles, and many other military and commercial applications. The electrochemical reserve-type batteries can in general be divided into two different basic types.

The first type includes the so-called thermal batteries, which are to operate at high temperatures. Unlike liquid reserve batteries, in thermal batteries the electrolyte is already in the cells and therefore does not require a release and distribution mechanism such as spinning. The electrolyte is dry, solid and non-conductive, thereby leaving the battery in a non-operational and inert condition. These batteries incorporate pyrotechnic heat sources to melt the electrolyte just prior to use in order to make them electrically conductive and thereby making the battery active. The most common internal pyrotechnic is a blend of Fe and KClO₄. Thermal batteries utilize a molten salt to serve as the electrolyte upon activation. The electrolytes are usually mixtures of alkali-halide salts and are used with the Li(Si)/FeS₂ or Li(Si)/CoS₂ couples. Some batteries also employ anodes of Li(Al) in place of the Li(Si) anodes. Insulation and internal heat sinks are used to maintain the electrolyte in its molten and conductive condition during the time of use.

Thermal batteries have long been used in munitions and other similar applications to provide a relatively large amount of power during a relatively short period of time, mainly during the munitions flight. Thermal batteries have high power density and can provide a large amount of power as long as the electrolyte of the thermal battery stays liquid, thereby conductive. The process of manufacturing thermal batteries is highly labor intensive and requires relatively expensive facilities. Fabrication usually involves costly batch processes, including pressing electrodes and electrolytes into rigid wafers, and assembling batteries by hand. The batteries are encased in a hermetically sealed metal container that is usually cylindrical in shape.

The second type includes the so-called liquid reserve batteries in which the electrodes are fully assembled for cooperation, but the liquid electrolyte is held in reserve in a separate container until the batteries are desired to be activated. In these types of batteries, by keeping the electrolyte separated from the battery cell, the shelf life of the batteries is essentially unlimited. The battery is activated by transferring the electrolyte from its container to the battery electrode compartment (hereinafter referred to as the “battery cell”).

A typical liquid reserve battery is kept inert during storage by keeping the aqueous electrolyte separate in a glass or metal ampoule or in a separate compartment inside the battery case. The electrolyte compartment may also be separated from the electrode compartment by a membrane or the like. Prior to use, the battery is activated by breaking the ampoule or puncturing the membrane allowing the electrolyte to flood the electrodes. The breaking of the ampoule or the puncturing of the membrane is achieved either mechanically using certain mechanisms usually activated by the firing setback acceleration or by the initiation of certain pyrotechnic material. In these batteries, the projectile spin or a wicking action is generally used to transport the electrolyte into the battery cells.

Reserve batteries are inactive and inert when manufactured and become active and begin to produce power only when they are activated. Reserve batteries have the advantage of very long shelf life of up to 20 years that is required for munitions applications.

Thermal batteries generally use some type of initiation device (igniter) to provide a controlled pyrotechnic reaction to produce output gas, flame or hot particles to ignite the heating elements of the thermal battery. There are currently two distinct classes of igniters that are available for use in thermal batteries. The first class of igniter operates based on electrical energy. Such electrical igniters, however, require electrical energy, thereby requiring an onboard battery or other power sources with related shelf life and/or complexity and volume requirements to operate and initiate the thermal battery. The second class of igniters, commonly called “inertial igniters,” operate based on the firing acceleration. The inertial igniters do not require onboard batteries for their operation and are thereby often used in munitions applications such as in gun-fired munitions and mortars.

Inertial igniters are also used to activate liquid reserve batteries through the rupture of the electrolyte storage container or membrane separating it from the battery core. The inertial igniter mechanisms may also be used to directly rupture the electrolyte storage container or membrane.

Inertial igniters used in munitions must be capable of activating only when subjected to the prescribed setback acceleration levels and durations and not when subjected to any of the so-called no-fire conditions such as accidental drops or transportation vibration or the like. This means that safety in terms of prevention of accidental ignition is one of the main concerns in inertial igniters.

In recent years, new improved chemistries and manufacturing processes have been developed that promise the development of lower cost and higher performance thermal and liquid reserve batteries that could be produced in various shapes and sizes, including their small and miniaturized versions.

Mechanical inertial igniters have been developed for many munitions applications in which the munitions are subjected to relatively high firing setback accelerations of generally over 1,000 Gs with long enough duration that provides enough time for the inertial igniter to activate the igniter pyrotechnic material, which may consist of a primer or an appropriate pyrotechnic material that is directly applied to the inertial igniter as described in previous art (for example, U.S. Pat. Nos. 9,160,009, 8,550,001, 8,931,413, 7,832,335 and 7,437,995, the contents of which are hereby considered included by reference).

In some munition applications, the setback acceleration duration is not long enough for inertial igniters without preloaded springs to either activate or to provide the required percussion impact to initiate the pyrotechnic material of the device (such as a percussion primer or directly applied pyrotechnic materials).

In some other munition applications, the setback acceleration level is not high enough and/or the striker mass of the inertial igniter cannot be made large enough due to the inertial igniter size limitations and/or the striker mass cannot be provided with long enough travel path due to the inertial igniter height limitations so that the striker mass cannot gain enough speed to impact the percussion primer or the directly applied pyrotechnic material with the required mechanical energy to initiate them.

For such applications, the mechanical inertial igniter must be provided with a source of mechanical energy to accelerate the striker element of the inertial igniter to gain enough kinetic energy to initiate the provided percussion primer or the directly applied pyrotechnic material of the device.

In some other munition applications, the setback acceleration level is low, sometimes in the order of 10-20 G and its duration is relatively long, sometimes of the order of 50-100 msec or more that must be differentiated from other accidental no-fire conditions.

Inertia-based igniters must provide two basic functions. The first function is to provide the capability to differentiate the accidental events such as drops over hard or soft surfaces or transportation vibration or the like, i.e., all no-fire events, from the prescribed firing setback acceleration (all-fire) event. In inertial igniters, this function is performed by keeping the device striker fixed to the device structure during all no-fire events until the prescribed firing setback acceleration event is detected. At which time, the device striker is released.

The second function of an inertia-based igniter is to provide the means of accelerating the device striker to the kinetic energy level that is needed to initiate the provided percussion primer or other device pyrotechnic material as it (hammer element) strikes an “anvil” over and around which the pyrotechnic material is provided. In general, the striker is provided with a relatively sharp point which strikes the pyrotechnic material covering a raised surface over the anvil, thereby allowing a relatively thin pyrotechnic layer to be pinched to achieve a reliable ignition mechanism. In many applications, percussion primers are directly mounted on the anvil side of the device and the required initiation pin is machined or attached to the striker to impact and initiate the primer. In either design, exit holes are provided on the inertial igniter to allow the reserve battery activating flames and sparks to exit.

Two basic methods are currently available for accelerating the device striker to the needed velocity (kinetic energy) level. The first method is based on allowing the setback acceleration to accelerate the striker mass following its release. This method requires the setback acceleration to be relatively high and have long enough duration to allow for the time that it takes for the striker mass to be released and for the striker mass to be accelerated to the required velocity before pyrotechnic impact. In addition, the striker mass must have enough space to travel so that it could gain the required velocity, which means that the inertial igniter must be allowed to have the required height (here, height is intended to be measured in the direction of the firing acceleration). As a result, this method is generally applicable to larger caliber and mortar munitions in which the setback acceleration is high, and duration is relatively long and in the order of 10-15 milliseconds. This method is also suitable for impact induced initiations in which the impact induced decelerations are high and have relatively long duration.

The second method relies on potential energy stored in a spring (elastic) element, which is then released upon the detection of the prescribed all-fire conditions. This method is suitable for use in munitions that are subjected to very low firing acceleration levels, such as in the order of 10-20 G, or very short setback accelerations, such as those of the order of 1-2 milliseconds. or when the setback acceleration level is low and space constraints does now allow the use of relatively large striker mass or where the height limitations of the available space for the inertial igniter does not provide enough travel distance for the inertial igniter striker to gain the required velocity and thereby kinetic energy to initiate the pyrotechnic material.

Inertia-based igniters must therefore comprise two components so that together they provide the mechanical safety, the capability to differentiate the prescribed all-fire condition from all no-fire conditions, and to provide the required striking action to achieve ignition of the pyrotechnic elements. The function of the safety system is to keep the striker element in a relatively fixed position until the prescribed all-fire condition (or the prescribed impact induced deceleration event) is detected, at which time the striker element is to be released, allowing it to accelerate toward its target under the influence of the remaining portion of the setback acceleration or the potential energy stored in its spring (elastic) element of the device. The ignition itself may take place because of striker impact, or simply contact or proximity. For example, the striker may be akin to a firing pin and the target akin to a standard percussion cap primer. Alternately, the striker-target pair may bring together one or more chemical compounds whose combination with or without impact will set off a reaction resulting in the desired ignition.

An example of the above second method of initiating the inertial igniter that relies on potential energy stored in a spring (elastic) element, which is then released upon the detection of the prescribed all-fire conditions, is the prior art inertial igniter embodiment 300 of FIGS. 1-5.

The full isometric view of the prior art inertial igniter embodiment 300 is shown in FIG. 1. The inertial igniter 300 is constructed with igniter body 301 and the cap 302 (FIG. 3), which is attached to the body 301 with the screws 303 (FIG. 3) through the tapped holes 336. When needed, an access hole 304 is provided for an arming pin to prevent accidental activation of the inertial igniter while handling or accidental drop or the like before assembly into the intended reserve battery or the like.

The top view of the inertial igniter 300 of FIG. 1 with its cap 302 removed is shown in the schematic of FIG. 2. The cross-sectional view B-B (FIG. 2) of the inertial igniter 300 is also shown in the schematic of FIG. 3. In the cross-sectional view of FIG. 3, the cap 302 of the inertial igniter 300 is also shown. In the top view of FIG. 2, the release lever 318 and its rotary joint pin 319 (shown in FIGS. 1 and 3) and striker mass engagement pin 321 as shown engaged with the provided surface on the striker mass 305 (see also FIG. 3) are shown.

As can be seen in the top view of FIG. 3 of the inertial igniter with the cap 302, the inertial igniter is provided with the striker mass 305, which is rotatable about the axis of the shaft 307. The striker mass 305 and shaft 307 assembly is shown in the cross-sectional view A-A (see FIG. 2) of FIG. 4. As can be seen in the cross-sectional view A-A of FIG. 4, the striker mass 305 is free to rotate about the shaft 307 by the provided clearance in the passing hole 313 in the body of the striker mass 305. On both sides of the striker mass 305, bushings 306 are provided to essentially fill the gap between the shaft 307 and both wound sides of the torsion spring 309. The bushings 306 are provided with enough clearance with the torsion spring 309 to allow its free rotational movement with minimal friction. The bushings 306 are also provided to constrain radial movement of the torsion spring 309 as it is preloaded and released to activate the inertial igniter as described later.

The shaft 307 is mounted onto the inertial igniter body 301 through the holes 308 in the wall 314 of the inertial igniter body, FIGS. 1 and 4. The shaft 307 is fitted in the holes 308 tightly to prevent it from sliding out of the inertial igniter body.

The two wound halves of the torsional spring 309 are mounted over the shaft 307 over the sleeves 306 as can be seen in the top view of FIG. 2 and the cross-sectional view of FIG. 4, with the “U” section 310 of the torsion spring 309 engaging the provided mating surface 311 of the striker mass 305 as can be seen in the top view of FIG. 2 and more clearly in the cross-sectional view of FIG. 3. The free legs 312 of the torsion spring 309 rests against the bottom surface 315 as the torsion spring 309 is preloaded in its pre-activation state as shown in FIG. 4. Alternatively, the free legs 312 of the torsion spring 309 may be positioned to rest against the inside surface of the cap 302 (not shown).

In the cross-sectional view of the inertial igniter 300 shown in its pre-activation state in FIG. 3, the striker mass release lever 318 and its striker mass engagement pin 321 are shown in their pre-loaded state. It is appreciated by those skilled in the art that in the configuration shown in FIG. 3, the clockwise rotation of the striker mass (as seen in the view of FIG. 3) by the preloaded torsional spring 309 is prevented by the striker mass engagement pin 321 of the release lever 318 as described later. It is noted that in the pre-activation configuration shown in the cross-sectional view of FIG. 3, the free-ends 312 of the torsional spring 309 are pressing against the bottom surface 315 of the inertial igniter body 301, FIG. 4, on one end and tend to rotate the striker mass 305 in the clockwise direction about the shaft 307 as viewed in the schematic of FIG. 3 via its “U” shaped portion, which is engaged with matching surfaces 311 of the striker mass 305, FIG. 2, on the other end. In the pre-activation configuration of FIG. 3, the striker mass engagement pin 321 of the release lever 318 is shown to prevent clockwise rotation of the striker mass 305 as described below, thereby forcing the striker mass 305 to remain in it illustrated configuration, thereby keeping the torsional spring 309 in its pre-loaded state.

As can be seen in the cross-sectional schematic of FIG. 3, which shows the state of the inertial igniter 300 in its pre-activation state, the inertial igniter is provided with a release lever 318. The release lever 318 is connected to the inertial igniter body 301 via the rotary joint provided by the pin 319 passing through the hole 320 across the length of the release lever 318—along the line perpendicular to the plane of the cross-sectional view of FIG. 3. The pin 319 is firmly mounted in the holes 328 (FIG. 1), while the mating hole 320 in the release lever 318 is provided with minimal clearance to allow for unimpeded rotation (clockwise and counterclockwise as viewed in the cross-sectional view of FIG. 3). Alternatively, ball bearings or low friction bushings may be used at this joint.

The striker mass engagement pin 321 is mounted onto the release lever 318 as shown in the schematic of FIG. 1, in which the protruding sides 329 of the release lever is provided with the holes 322, in which the striker engagement pin 321 is assembled. In the schematic of FIG. 1, the striker mass engagement pin 321 in shown to be mounted in the provided holes 322 of the release lever 318 via ball bearings 323 to minimize resistance to its rotation relative to the release lever 318. As it is described later in this enclosure, the striker engagement pin 321 rotation relative to the release lever 318 is desired to generate minimal resistance due to friction between their mating surfaces to minimize variation in the inertial igniter activation acceleration levels.

In the pre-activation configuration of the inertial igniter 300 shown in the schematic of FIG. 3, the striker engagement pin 321 of the release lever 318 is shown to be positioned over the provided curved surfaces 316 (FIG. 3 and under pin 321 in FIG. 2), resisting the force applied by the preloaded torsional spring 309 via the striker mass 305, thereby keeping the inertial igniter in its pre-activation state shown in FIG. 3.

The force applied by the striker mass 305 to the striker mass engagement pin 321 via the striker mass surfaces 316 is prevented from rotating the release lever in the counterclockwise direction and thereby pushing the striker mass engagement pin 321 to the left as seen in the cross-sectional view of FIG. 3, which would then release the striker mass 305 to rotate in the clockwise direction by the preloaded torsional spring 309. This is accomplished using one or more of the following methods. The features enabling these methods to maintain the striker mass 305 in its pre-activation state shown in FIG. 3 are also used to design inertial igniters to the prescribed no-fire and all-fire condition requirements of each application.

The first method that can be used to keep the inertial igniter in its pre-activation state is based on the use of the curvature of the striker mass surfaces 316 that engages the striker mass engagement pin 321 of the release lever 318, FIG. 3. In this method, lips 317 are provided on the striker mass surfaces 316 as shown in the schematic of FIG. 3. As a result, for the striker mass engagement pin 321 of the release lever 318 to disengage the striker mass surfaces 316, i.e., to rotate in the counterclockwise direction as viewed in FIG. 3, the striker mass engagement pin must force rotation of the striker mass 305 in the counterclockwise direction as viewed in FIG. 3, i.e., it must increase the preloading level of the torsional spring 309. As a result, the inertial igniter would stay in its pre-activation state shown in FIG. 3.

The second method that can be used to keep the inertial igniter in its pre-activation state is based on the provision of at least one elastic element (spring) element to bias the release lever 318 in the direction of clockwise rotation. As an example, the biasing preloaded compressive spring 325 may be positioned between the release lever 318 and the bottom surface 315 of the inertial igniter body 301 as shown in the schematic of FIG. 3. The spring 325 can be positioned in a pocket 324 to keep from moving out of position. It is appreciated by those skilled in the art that many different spring types may also be used for the indicated clockwise rotation biasing of the release lever 318 as seen in the view of FIG. 3.

It is noted that the acceleration of the inertial igniter 300 in the direction of the arrow 330 shown in FIG. 3 would act on the inertia of the release lever 318 and apply a downward force at its center of mass equal to the product of its mass and the acceleration in the direction of the arrow 330, which would tend to rotate the release lever 318 in the counterclockwise direction. The rotation of the release lever 318 is, however, resisted by the biasing force of the preloaded compressive spring 325 and the required counterclockwise rotation of the striker mass 305 in order for the striker mass engagement pin 321 to be able to travel leftward due to the rotation of the release lever 318 about the pin 319. It is appreciated that for the pin 321 to move to the left in the direction of releasing the striker mass 305, it must push the lips 317 of the striker mass surfaces 316 downwards, thereby forcing the striker mass 305 to undergo the required amount of counterclockwise rotation, which would in turn provide resistance to counterclockwise rotation of the release lever 318.

It is therefore appreciated that the level of acceleration of the inertial igniter 300 that is needed for the release lever 318 to rotate the required amount in the counterclockwise direction for the striker mass engagement pin 321 to disengage the striker mass 305 and thereby allow it to be freely accelerated in the clockwise direction can be varied by varying one or more of the following parameters to match a prescribed all-fire acceleration level and duration thresholds. The all-fire acceleration level threshold can be reduced by varying one or more of the following inertial igniter parameters: (a) reducing the preloading of the compressive spring 325 and its rate, (b) increasing the moment of inertia of the release lever 318 about the axis of the 319, (c) reducing the extent of the lips 317, i.e., the amount of counterclockwise rotation of the striker mass 305 that is required for striker mass engagement pin 321 to release the striker mass; and (d) by positing the pin 319 laterally relative to the striker mass engagement pin 321 as viewed in FIG. 3 in the pre-activation configuration of the inertial igniter 300 to minimize the amount of counterclockwise rotation of the striker mass 305 that is required for the striker mass engagement pin 321 to release the striker mass. The all-fire duration threshold for the activation of the inertial igniter 300 at a prescribed acceleration level can be reduced by varying one or more of the following inertial igniter parameters: (a) by reducing the preloading of the compressive spring 325 and its rate; (b) by increasing the moment of inertia of the release lever 318 about the axis of the 319; and (3) varying the striker mass engagement pin 321 and the striker mass surfaces 316 and the lips 317 geometries to reduce the amount of counterclockwise rotation of the release lever 318 that is required for the striker mass 305 to be released. The opposite changes in the inertial igniter 300 parameters would have the opposite effect.

Now, when the inertial igniter 300 is accelerated in the direction of the arrow 330, FIG. 3, as the prescribed acceleration level threshold and duration is reached, the release lever 318 is rotated in the counterclockwise direction until the striker mass engagement pin 321 moves far enough to the left and pass over the lips 317, thereby releasing the striker mass 305. At this point, the stored mechanical (potential) energy in the torsional spring 309 would begin to rotationally accelerate the striker mass 305 in the clockwise direction about the axis of the shaft 307. The striker mass 305 is thereby accelerated in the clockwise direction until the percussion pin 331 strikes the percussion primer 332 and causing it to initiate as shown in the cross-sectional view of FIG. 5. It is noted that in the cross-sectional view of FIG. 5, the inertial igniter cap 302 containing the percussion primer 332 with the provided flame exit hole 333 are shown. The release lever 318, FIG. 3, in its released position as indicated by the numeral 337 is also shown in the cross-sectional view of FIG. 5, thereby providing a complete cross-sectional view of the inertial igniter 300 in its post-activation state. In this state, the biasing elastic element (spring) 325, FIG. 3, is shown to be compressively deformed and indicated by the numeral 328.

Once the percussion primer 332 is initiated, the flames and sparks generated by the initiation of the primer 332 would then exit from the hole 333 in the inertial igniter cap 302, FIGS. 3 and 5. The cross-sectional view of the inertial igniter 300 in this post-activation configuration is shown in FIG. 5. The hole 333 at the center of the cap 302, FIG. 3, is provided for the exiting primer or other pyrotechnic material generated flames and sparks upon the inertial igniter activation.

It is appreciated that the pre-activation torsional preloading level of the torsional spring 309 and its spring rate must be high enough and the range of rotation of the striker mass 305 from its pre-activation (FIG. 3) to its post-activation positions must be large enough so that the striker mass 305 would gain enough kinetic energy after its release so that as it impacts the percussion primer 332 (FIG. 5) as was previously described it would initiate the percussion primer.

It is also appreciated by those skilled in the art that the percussion primer or other pyrotechnic material that is to be initiated to activate the reserve battery must be kept sealed from elements to ensure proper operation of the percussion primer or the pyrotechnic material that is used and to ensure the require shelf life of the assembled reserve battery and the striker mechanism.

The shortcomings of the prior art mechanical inertial igniters are related to their following limitations for the following applications in munitions and the like:

• • 1. They are not capable of detecting relatively long duration firing accelerations of the order of 50-100 milliseconds or longer,
  • 2. Their required height and overall size are generally significantly larger than are desired for munitions applications, particularly when the firing acceleration is low,
  • 3. They are not capable of detecting long duration firing or impact accelerations when the acceleration levels are relatively high.

In addition, due to the unavoidable friction related forces, the difference between the no-fire impulse due to the acceleration level and duration acting on the striker mass release mechanism and the all-fire impulse due to the setback acceleration level and its duration acting on the striker mass release mechanism must be large enough to ensure the high reliability that is required for the proper operation of the inertial igniters. In most munitions, operational reliability requirement of sometimes over 99.9 percent at 95 percent confidence level is common and in certain cases must be even higher. In munitions in which the difference between no-fire and all-fire acceleration levels acting on the striker mass release mechanism is relatively small, the friction forces between the relevant moving parts of the inertial igniter must therefore be minimized.

It is also appreciated by those skilled in the art that currently available G-switches of different type that are used for opening or closing an electrical circuit are configured to perform this function when they are subjected to a prescribed acceleration level without accounting for the duration of the acceleration level. As such, they suffer from the shortcoming of being activated accidentally, e.g., when the object in which they are used is subjected to short duration shock loading such as could be experienced when dropped on a hard surface as was previously described for the case of inertial igniter used in munitions.

When used in applications such as in munitions, it is highly desirable for G-switches to be capable to differentiate the accidental and short duration shock (acceleration) events such as those experienced by dropping on hard and soft surfaces, i.e., all no-fire conditions, from significantly longer duration firing setback (shock) accelerations, i.e., all-fire condition. Such G-switches should activate when firing setback (all-fire) acceleration and its duration results in an impulse level threshold corresponding to the all-fire event has been reached, i.e., they must operate as an “impulse switch”. This requirement necessitates the employment of safety mechanisms like those used in the inertial igniter embodiments, which can allow the switch activation only when the firing setback acceleration level and duration thresholds have been reached. The safety mechanism can be thought of as a mechanical delay mechanism, after which a separate electrical switch mechanism is actuated or released to provide the means of opening or closing at least one electrical circuit.

SUMMARY

A need therefore exists for methods to design mechanical inertial igniters for munitions applications and the like in which the setback acceleration levels are low, sometimes in the order of 10-20 Gs, while its duration is long, sometimes in the order of 50-100 milliseconds or more, and due to space limitations, the inertial igniter must be relatively compact and small. In addition, the inertial igniters are required to be highly reliable, for example, have better than 99.9 percent reliability with 95 percent confidence level.

A need also exists for mechanical inertial igniters that are developed based on the above methods and that can satisfy the safety requirement of munitions, i.e., the no-fire conditions, such as accidental drops and transportation vibration and other similar events.

A need therefore exists for novel miniature mechanical inertial igniters for reserve batteries such as thermal and liquid reserve batteries used in munitions such as rockets and missiles and gun-fired munitions and mortars and the like, that could be used in fuzing and other similar applications, that are safe (i.e., satisfy the munitions no-fire conditions), are small, and that can be used in applications in which the setback acceleration level is low (for example, tens of Gs) and/or the setback acceleration duration is long (for example, in the order of 50-100 milliseconds or more).

A need also exists for mechanical inertial igniters that are developed based on the above methods and that can satisfy the safety requirement of munitions, i.e., the no-fire conditions, such as accidental drops and transportation vibration and other similar events, and that once subjected to such accidental conditions, its mechanisms remains functional and reset to or close to its configuration prior to experiencing such accidental (no-fire) events.

To ensure safety and reliability, inertial igniters should not initiate during acceleration events which may occur during manufacture, assembly, handling, transport, accidental drops, etc. Additionally, once under the influence of an acceleration profile particular to the intended firing of ordinance, the device should initiate with high reliability.

In addition, the inertial igniters used in munitions are generally required to have a shelf life of better than 20 years and could generally be stored at temperatures of sometimes in the range of −65 to 165 degrees F. The inertial igniter designs must also consider the manufacturing costs and simplicity in the designs to make them cost effective for munitions applications.

Accordingly, methods are provided that can be used to design fully mechanical inertial igniters that can satisfy the prescribed no-fire requirements while satisfying relatively low all-fire setback acceleration level and long duration requirements. For initiation of percussion primer or other provided pyrotechnic materials, the methods rely on potential energy stored in a spring (elastic) element, which is then released upon the detection of the prescribed all-fire conditions. These methods are particularly suitable for use in munitions that are subjected to very low setback accelerations with very long durations, particularly in the presence of available space constraints.

Also provided are fully mechanical igniters that are configured based on the above methods that can satisfy the prescribed no-fire requirements while satisfying relatively low all-fire firing setback acceleration level and long duration requirements.

For initiation of percussion primer or other provided pyrotechnic materials, the methods rely on potential energy stored in a spring (elastic) element, which is then released upon the detection of the prescribed all-fire conditions. These methods are particularly suitable for use in munitions that are subjected to very low setback accelerations with very long durations, particularly in the presence of available space constraints.

Also provided is a method for initiating reserve thermal batteries. The method comprising: releasing a striker mass upon an acceleration duration and magnitude greater than a prescribed threshold; and transferring potential energy stored in an elastic element (spring element) to the striker mass to gain enough kinetic energy to strike and initiate the provided percussion cap or pyrotechnic material.

The method also comprises a mechanism that releases the striker mass only upon an acceleration duration and magnitude greater than a prescribed threshold (all-fire condition).

Those skilled in the art will appreciate that the inertial igniters disclosed herein may provide one or more of the following advantages over prior art inertial igniters:

• • Provide inertial igniters that are safe and can differentiate no-fire conditions from all-fire conditions based on the prescribed all-fire setback acceleration level (target impact acceleration level when used for target impact activation) and its prescribed duration.
  • Provide inertial igniters that can be activated by log G setback acceleration levels with relatively long durations.
  • Provide inertial igniters that are very short in height to minimize the space that is occupied by the inertial igniter in the reserve battery and other locations that they are used, which is made possible by separating the striker mass release mechanism from the mechanism that accelerates the striker element, i.e., the use of potential energy stored in the device elastic element.
  • Provide inertial igniters that allow the use of standard off-the-shelf percussion cap primers.

Accordingly, an inertial igniter is provided. The inertial igniter comprising: a striker mass movable towards one of a percussion primer or pyrotechnic material; a striker mass release element for releasing the striker mass to strike the percussion primer or pyrotechnic material upon an acceleration time and magnitude greater than a prescribed threshold.

The inertial igniter further comprises a mechanical delay mechanism for releasing the striker mass when the prescribed all-fire acceleration threshold level persists for the prescribed period and essentially resetting to its initial configuration if the prescribed all-fire acceleration threshold level does not persist for the prescribed period.

The inertial igniter further comprises an elastic element (such as a torsion spring) that is preloaded to provide the required amount of potential energy to accelerate the striker mass to the required velocity to achieve reliable percussion cap or pyrotechnic material initiation upon impact.

The inertial igniter striker mass and the release element are rotationally movable to minimize the effects of friction on the operation of the inertial igniter.

The striker mass release element can be configured to be returnable from the path of releasing the striker mass when the acceleration duration and magnitude (all-fire condition) threshold is not reached.

The inertial igniter can also be provided with a safety pin that prevents its activation for the purpose of safety during transportation and assembly in the reserve battery or the like.

The inertial igniter can also be provided with an arm/disarm switch that when is set to the disarm position, it prevents its activation for the purpose of safety during transportation and assembly in the reserve battery or the like.

Also provided is a method for initiating a thermal battery. The method comprising: releasing a striker mass upon an acceleration duration and magnitude greater than a prescribed threshold; and transferring potential energy stored in an elastic element (spring element) to the striker mass to gain enough kinetic energy to strike and initiate the provided percussion cap or pyrotechnic material.

The method can further comprise returning the striker mass release element to its original (zero acceleration condition) position when the acceleration duration and magnitude (all-fire condition) threshold is not reached.

In certain munitions applications, if the munition is subjected to a very high acceleration shock loading, for example if it is dropped from a relatively high height that would subject the munition to a “very high G acceleration shock level event” that may even be orders of magnitude higher than the firing acceleration level, the igniter would be prevented from being activated. In certain such applications, the inertial igniter is required to be rendered non-functional, i.e., would not be initiated even if it is subjected to the prescribed activation acceleration level and duration. In other applications, the inertial igniter may be required to stay functional following such a “very high G acceleration shock level event”, i.e., initiate when subjected to the prescribed activation acceleration level and duration.

A need therefore exists for inertial igniters that when they are subjected to a “very high G acceleration shock level event”, they would prevent the inertial igniter from being initiated. The option is provided for inertial igniters that are rendered non-functional following such “very high G acceleration shock level events” or staying functional after such an event.

Accordingly, methods and devices are provided that can be used to configure fully mechanical inertial igniters that can satisfy the prescribed no-fire requirements while satisfying relatively low all-fire setback acceleration level and long duration requirements. For initiation of percussion primer or other provided pyrotechnic materials, the methods rely on potential energy stored in a spring (elastic) element, which is then released upon the detection of the prescribed all-fire conditions. These methods and devices are particularly suitable for use in munitions that are subjected to very low setback accelerations with very long durations, particularly in the presence of available space constraints. The methods and devices can also be used to prevent the inertial igniter from being activated when it is subjected to a “very high G acceleration shock level event”. Upon being subjected to a “very high G acceleration shock level event”, the inertial igniter may be required to be rendered non-functions, i.e., not initiate anymore even when subjected to the prescribed activation acceleration level and duration or may be required to stay functional and initiate when it is subsequently subjected to the prescribed activation acceleration level and duration event.

Also provided are fully mechanical igniters that are configured based on the above methods that can satisfy the prescribed no-fire requirements while satisfying relatively low all-fire firing setback acceleration level and long duration requirements.

Also provided are fully mechanical igniters that are configured based on the above methods that can satisfy the prescribed no-fire requirements while satisfying relatively low all-fire firing setback acceleration level and long duration requirements, while also prevent inertial igniter initiation if it is subjected to an aforementioned “very high G acceleration shock level event”. The inertial igniter may be configured such that it becomes non-functional following a “very high G acceleration shock level event” or may be configured to stay functional following such an event.

It is appreciated by those skilled in the art that the disclosed inertial igniter mechanisms may also be used to construct electrical impulse switches, which are activated like the so-called electrical G switches but with the added time delays to account for the activation shock level duration requirement, i.e., like the disclosed inertial igniters to activate when a prescribed shock loading (acceleration) level is experienced for a prescribed length of time (duration). The electrical “impulse switches” may be configured as normally open or closed and with or without latching mechanisms. Such impulse switch embodiments that combine such safety mechanisms with electrical switching mechanisms are described herein together with alternative methods of their construction.

Also disclosed are inertial igniters with the capability to open or close an electrical switch, which can then be used by the user to determine the activation status of the inertial igniter as assembled in the reserve battery or the like. This capability may also be used for all-fire event detection in munitions or the like.

A need therefore exists for novel miniature impulse switches for use in munitions or the like that can differentiate accidental short duration shock loading (so-called no-fire events for munitions) from generally high but longer duration, i.e., high impulse threshold levels, that correspond to all-fire conditions in gun fired munitions or the like. Such impulse switches must be small in size and volume to make them suitable for being integrated into electronic circuit boards or the like. They must also be readily scalable to different all-fire and no-fire conditions for different munitions, particularly for low G setback acceleration with relatively long duration. Reliability is also of much concern since most munitions are required to have a shelf life of up to 20 years and could generally be stored at temperatures of sometimes in the range of −65 to 165 degrees F. This requirement is usually satisfied best if the device is in a sealed compartment. The impulse switch must also consider the manufacturing costs and simplicity of design to make it cost effective for munitions applications.

Those skilled in the art will appreciate that the compact impulse-based electrical impulse switches disclosed herein may provide one or more of the following advantages over prior art electrical G-switches:

• • Provide impulse-based electrical G-switches that are relatively small in both height and volume,
  • Provide impulse-based electrical switches that differentiate all-fire conditions from all no-fire conditions, even those no-fire conditions that result in low setback acceleration levels with relatively long duration, thereby eliminating the possibility of accidental activation,
  • Provide electrical impulse switches that are modular in design and can therefore be readily customized to different no-fire and all-fire requirements,
  • Provide impulse switches that may be normally open or normally closed and that are modular in design and can be readily customized for opening or closing or their combination of at least one electric circuit.

Accordingly, impulse-based impulse switches with modular design for use in electrical or electronic circuitry are provided that activate upon a prescribed acceleration profile threshold. In most munition applications, the acceleration profile is usually defined in terms of firing setback acceleration and its duration.

BRIEF DESCRIPTION OF THE DRAWINGS

These and other features, aspects, and advantages of the apparatus will become better understood with regard to the following description, appended claims, and accompanying drawings where:

FIG. 1 illustrates a schematic of the isometric drawing of a prior art inertial igniter operating with stored potential energy.

FIG. 2 illustrates a schematic of the top view of the prior art inertial igniter of FIG. 1 with its cap removed to show the internal components of the device. The striker mass element release arm and its inertial igniter body attached shaft are also removed for clarity.

FIG. 3 illustrates a schematic of a cross-sectional view of the prior art inertial igniter of FIG. 1 in its pre-activation state with the inertial igniter cap assembly removed for clarity.

FIG. 4 illustrates the cross-sectional view A-A indicated in the top view of FIG. 2 of the inertial igniter.

FIG. 5 illustrates the schematic of the cross-sectional view of the prior art inertial igniter of FIG. 1 in its post-activation state.

FIG. 6A illustrates the schematic of the first inertial igniter mechanism embodiment of the present invention for low setback accelerations with long durations.

FIG. 6B illustrates the schematic of the first inertial igniter mechanism embodiment of FIG. 6A as subjected to setback threshold or higher acceleration level and the delay mechanism mass is displaced and released.

FIG. 6C illustrates the schematic of the first inertial igniter mechanism embodiment of FIG. 6A as the striker mass release mechanism actuation member of the delay mechanism is released.

FIG. 6D illustrates the schematic of the first inertial igniter mechanism embodiment FIG. 6A as the striker mass is released by the actuation of its release mechanism by the delay mechanism mass.

FIG. 7A illustrates the schematic of the first modified inertial igniter of FIG. 6A to prevent ignition before the prescribed duration of the acceleration threshold has elapsed.

FIG. 7B illustrates the schematic of the modified inertial igniter of FIG. 7A configuration when the prescribed acceleration threshold has ceased before its prescribed duration has elapsed.

FIG. 8A illustrates the striker mass release member together with the striker mass mechanism component of the inertial igniter embodiment of FIG. 6B as indicated by an enclosed dashed-lines area.

FIG. 8B illustrates the striker mass release member together with the striker mass mechanism component of FIG. 8A as the inertial igniter is subjected to the prescribed acceleration threshold.

FIG. 9A illustrates the schematic of the second inertial igniter mechanism embodiment of the present invention for low setback accelerations with long durations.

FIG. 9B illustrates the schematic of the second inertial igniter mechanism embodiment of FIG. 9A as subjected to setback threshold or higher acceleration level and the delay mechanism mass is displaced and released.

FIG. 9C illustrates the schematic of the second inertial igniter mechanism embodiment of FIG. 9A as the delay mechanism mass begins to pass the striker mass release mechanism lever.

FIG. 9D illustrates the schematic of the second inertial igniter mechanism embodiment of FIG. 9A as the delay mechanism mass passes the striker mass release mechanism lever.

FIG. 9E illustrates the schematic of the second inertial igniter mechanism embodiment FIG. 9A as the delay mechanism mass engages the striker mass release mechanism lever as it returns from its rightmost displacement.

FIG. 9F illustrates the schematic of the second inertial igniter mechanism embodiment FIG. 9A as the striker mass is released by the actuation of its release mechanism by the delay mechanism mass.

FIG. 10 illustrates the schematic of the first modified inertial igniter of FIG. 9A to prevent ignition before the prescribed duration of the acceleration threshold has elapsed.

FIG. 11A illustrates the schematic of the second modified inertial igniter of FIG. 9A to prevent ignition before the prescribed duration of the acceleration threshold has elapsed.

FIG. 11B illustrates the schematic of the modified inertial igniter of FIG. 11A as it is subjected to the prescribed acceleration threshold.

FIG. 12 illustrates a schematic view of the normally open impulse switch embodiment for closing electrical circuits when subjected to a prescribed all-fire or the like condition in its non-activated state.

FIG. 13 illustrates a schematic view of the normally open impulse switch embodiment of FIG. 12 for closing electrical circuits in its activated state after having been subjected to a prescribed all-fire or the like condition.

FIG. 14 illustrates a schematic view of the normally closed impulse switch embodiment for closing electrical circuits when subjected to a prescribed all-fire or the like condition in its non-activated state.

FIG. 15 illustrates a schematic view of the normally closed impulse switch embodiment of FIG. 13 for closing electrical circuits in its activated state after having been subjected to a prescribed all-fire or the like condition.

FIG. 16 illustrates the schematic of an “inertial igniter with activation state indicating sensor” embodiment of the present invention constructed with the inertial igniter of FIG. 9A with an integrated normally open impulse switch.

FIG. 17 illustrates the schematic of the lateral and spin acceleration and spin velocity insensitive mechanical delay mechanism embodiment for use in inertial igniters.

FIG. 18A illustrates the frontal view “A” of the lateral and spin acceleration and spin velocity insensitive mechanical delay mechanism embodiment of FIG. 17.

FIG. 18B illustrates the frontal view “A” of the lateral and spin acceleration and spin velocity insensitive mechanical delay mechanism embodiment of FIG. 17 while being subjected to the prescribed acceleration and winding the spring of the mechanical delay mechanism embodiment of FIG. 17.

FIG. 18C illustrates the frontal view “A” of the lateral and spin acceleration and spin velocity insensitive mechanical delay mechanism embodiment of FIG. 17 as completes winding the spring of the mechanical delay mechanism embodiment of FIG. 17 and releases it to begin its torsional oscillatory motion.

FIG. 18D illustrates the frontal view “A” of the lateral and spin acceleration and spin velocity insensitive mechanical delay mechanism embodiment of FIG. 17 used to actuate a striker release lever of an inertial igniter.

FIG. 18E illustrates the frontal view “A” of the lateral and spin acceleration and spin velocity insensitive mechanical delay mechanism embodiment of FIG. 17 with a modified release lever of FIG. 18D to increase the mechanism delay time.

FIG. 19 illustrates the schematic of another lateral and spin acceleration and spin velocity insensitive long duration mechanical inertial igniter embodiment.

FIG. 20A illustrates the top view of the inertial spring winding component of the lateral and spin acceleration and spin velocity insensitive long duration mechanical inertial igniter embodiment of FIG. 19.

FIG. 20B illustrates the cross-sectional view C-C of FIG. 20A, showing the side view of the first inertially actuating link member of the inertial spring winding component of the inertial igniter embodiment of FIG. 19.

FIG. 20C illustrates the cross-sectional view D-D of FIG. 20A, showing the side view of the second inertially actuating link member of the inertial spring winding component of the inertial igniter embodiment of FIG. 19 after it has been moved to its actuation positioning by the first inertially actuated link member of the inertial spring winding component of the inertial igniter.

FIG. 20D illustrates the top view of two inertially actuating units of the inertial spring winding component of the inertial igniter embodiment of FIG. 19 with separate shafts that are connected by a one-way clutch or the like.

FIG. 21A illustrates the top view of an alternative inertial spring winding component of the lateral and spin acceleration and spin velocity insensitive long duration mechanical inertial igniter embodiment of FIG. 19.

FIG. 21B illustrates the cross-sectional view E-E of FIG. 21A, showing the side view of the first inertially actuating “gear section” and mass member assembly of the inertial spring winding component of the inertial igniter embodiment of FIG. 19.

FIG. 21C illustrates the cross-sectional view E-E of FIG. 21A, showing the positioning of the first inertially actuating “gear section” and mass member assembly as it is rotated fully in the clockwise direction due to the applied activation acceleration.

FIG. 21D illustrates the cross-sectional view F-F of FIG. 21A, showing the side view of the second inertially actuating “gear section” and mass member assembly of the inertial spring winding component of the inertial igniter embodiment of FIG. 19.

FIG. 22 illustrates the top view of the mechanical delay component of the lateral and spin acceleration and spin velocity insensitive long duration mechanical inertial igniter embodiment of FIG. 19.

FIG. 22A illustrates the cross-sectional view G-G of FIG. 22, showing the components of the “spring winding rotation” mechanism and its engaging gear member of the mechanical delay mechanism component of the lateral and spin acceleration and spin velocity insensitive long duration mechanical inertial igniter embodiment of FIG. 19.

FIG. 22B illustrates the cross-sectional view G-G of FIG. 22 as the “spring winding rotation” mechanism rotates the gear member of the mechanical delay mechanism component and winds its torsion spring.

FIG. 22C illustrates the cross-sectional view G-G of FIG. 22 as the “spring winding rotation” mechanism rotates the gear member of the mechanical delay mechanism component and winds its torsion spring and begins the process of releasing the gear member.

FIG. 22D illustrates the cross-sectional view G-G of FIG. 22 as the “spring winding rotation” mechanism rotates the gear member of the mechanical delay mechanism component and winds its torsion spring and releases the gear member.

FIG. 23 illustrates the top view of a modified mechanical delay component of the embodiment of FIG. 22 for the lateral and spin acceleration and spin velocity insensitive long duration mechanical inertial igniter embodiment of FIG. 19.

FIG. 24 illustrates the top view of the modified mechanical delay component of the embodiment of FIG. 23 with the addition of a gearing to reduce the equivalent torsional spring rate of the rotationally oscillating (vibrating) system of the mechanical delay component of the inertial igniter embodiment of FIG. 19.

FIG. 25 illustrates the top view of the modified mechanical delay component of the embodiment of FIG. 23 with the addition of a gearing to increase the total moment of inertia of the rotationally oscillating (vibrating) system of the mechanical delay component of the inertial igniter embodiment of FIG. 19.

FIG. 26 illustrates the side view “H” of the initiator striker mechanism component of the inertial igniter embodiment of FIG. 19 and the striker releasing rotationally oscillating gear member.

FIG. 27 illustrates the rotationally oscillatory gear of the mechanical delay component of the inertial igniter embodiment of FIG. 19 in its configuration before being released to rotationally oscillate by the “spring winding rotation” mechanism of the mechanical delay component.

FIG. 28 illustrates the side view “H” of the initiator striker mechanism component of the inertial igniter embodiment of FIG. 19 of FIG. 26, following release of the inertial igniter striker member and its acceleration by its preloaded torsion spring to strike the percussion primer and initiate it.

FIG. 29 illustrates the rotationally oscillatory gear of the mechanical delay component of the inertial igniter embodiment of FIG. 19 in its initial configuration and before being released to rotationally oscillate by the “spring winding rotation” mechanism of the mechanical delay component and release the striker member of the inertial igniter.

FIG. 30 illustrates the side view “H” of a modified initiator striker mechanism component embodiment of FIG. 26 of the inertial igniter embodiment of FIG. 19 and the striker releasing rotationally oscillating gear member.

FIG. 31 illustrates the rotationally oscillatory gear of the modified mechanical delay component of the inertial igniter embodiment of FIG. 19 in its configuration before being released to rotationally oscillate by the “spring winding rotation” mechanism of the mechanical delay component.

FIG. 32 illustrates the side view “H” of the modified initiator striker mechanism component of the inertial igniter embodiment of FIG. 19 of FIG. 30, following release of the inertial igniter striker member and its acceleration by its preloaded torsion spring to strike the percussion primer and initiate it.

FIG. 33A illustrates the means of preventing actuation of the “spring winding component” of the inertial igniter embodiments of FIG. 19 if the activation acceleration is below the prescribed threshold level.

FIG. 33B illustrates the means of preventing actuation of the “spring winding component” of the inertial igniter embodiments of FIG. 19 if the inertial igniter is subjected to a “very high acceleration” event in the direction of the activation acceleration.

FIG. 34A illustrates the means of preventing actuation of the modified “spring winding component” of FIG. 21A of the inertial igniter embodiments of FIG. 19 if the activation acceleration is below the prescribed threshold level.

FIG. 34B illustrates the means of preventing actuation of the modified “spring winding component” of FIG. 21A of the inertial igniter embodiments of FIG. 19 if the inertial igniter is subjected to a “very high acceleration” event in the direction of the activation acceleration.

FIG. 35A illustrates the means of preventing rotation of the striker release member of the inertial igniter embodiment of FIG. 19 shown in FIG. 26 if the activation acceleration is below the prescribed threshold level.

FIG. 35B illustrates the means of preventing rotation of the striker release member of the inertial igniter embodiment of FIG. 19 shown in FIG. 26 if the inertial igniter is subjected to a “very high acceleration” event in the direction of the activation acceleration.

FIG. 36A illustrates the modified striker release mechanism of FIG. 30 which allows the inertial igniter embodiment of FIG. 19 to reset if the activation acceleration is below the prescribed threshold level.

FIG. 36B illustrates the modified striker release mechanism of FIG. 30 which allows the inertial igniter embodiment of FIG. 19 to reset if the inertial igniter is subjected to a “very high acceleration” event in the direction of the activation acceleration.

DETAILED DESCRIPTION

The inertial igniter embodiments of the present invention use striker mass members that are provided with pre-loaded spring (elastic) elements to provide stored potential energy to accelerate the striker mass with the required kinetic energy to initiate a percussion primer or other pyrotechnic material upon the release of the striker mass, as was described for the prior art inertial igniters of FIGS. 1-5. In normal conditions, the inertial igniters are provided with a locking mechanism that keeps their ignition pin away from the percussion primer. The locking mechanism is provided with a release mechanism that is activated once the inertial igniter is subjected to the prescribed all-fire condition, i.e., to the minimum setback acceleration for a minimum amount of time, at which time the preloaded spring would accelerate the striker mass to the required kinetic energy for its ignition pin to initiate the provided percussion primer upon impact.

In the embodiments of the present invention, the same method and similar mechanisms are used for in the design of the striker mass, its preloaded spring and striker mass release mechanism once the prescribed acceleration and duration thresholds are detected.

The inertial igniters are, however, provided with novel long delay mechanisms that ensure that the setback acceleration threshold level persist during the prescribed period (all-fire duration) before allowing the striker mechanism to be released. As a result, the prescribed minimum setback acceleration threshold and its duration for inertial igniter initiation is satisfied.

The methods to design the above novel long delay mechanisms inertial igniters are herein described through the following examples. It is appreciated by those skilled in the art that the delay mechanisms alone or as integrated with the aforementioned striker mass and its release mechanism must provide the means of ensuring that the inertial igniter is initiated only after the prescribed minimum setback acceleration threshold and its duration (all-fire condition) has been detected.

The basic method of designing a delay mechanism that can be used in inertial igniters to actuate the release mechanism of a striker mass with preloaded spring (elastic) member only after the prescribed minimum setback acceleration threshold and its duration (all-fire condition) has been detected is described by its application to the inertial igniter embodiment 10 shown in the schematic of FIG. 6A.

The inertial igniter 10 of FIG. 6A is provided with a spring loading mass 11, which is free to translate in a guide (shown as the rolling members 12) along the surface 13 of the inertial igniter body 14 (shown as ground) in the direction parallel to the direction of firing acceleration indicated by the arrow 15. The spring loading mass 11 is provided with a preloaded tensile spring 16, which is attached to the inertial igniter body 14 on one end and to the spring loading mass 11 on the other end as shown in FIG. 6A.

The inertial igniter 10 of FIG. 6A is also provided with a striker mass member 17, which is attached to the inertial igniter body 14 by the rotary joint 18. The striker mass member 17 is also provided with a preloaded compressive spring 19, which biases it to keep its tip 20 against the tip 21 of the striker mass release member 22 as shown in FIG. 6A. The striker mass release member 22 is also attached to the inertial igniter body 14 by the rotary joint 23, and is provided with a preloaded tensile spring 25, which bias it against the stop 24 on the inertial igniter body 14 as shown in the configuration of FIG. 6A. The striker mass member 17 is also provided with a sharp tip 26, which is configured to initiate the percussion primer 27 (or other appropriate pyrotechnic material) upon impact as described later.

The inertial igniter 10 of FIG. 6A is also provided with a delay mechanism mass 28, which is free to translate in a guide (shown as the rolling members 29) along the surface 30 of the inertial igniter body 14 (shown as ground) in the direction perpendicular to the direction of firing acceleration indicated by the arrow 15. The delay mechanism mass 28 is provided with the spring 31, which is attached to the inertial igniter body 14 on one end and to the delay mechanism mass 28 on the other end as shown in FIG. 6A. In normal conditions shown in FIG. 6A, the spring 31 is in its free length (unloaded) condition. The delay mechanism mass 28 is also provided with an extended member 32, which is configured to engage the tip 33 of the striker mass release member 22 as described later.

The inertial igniter embodiment 10 of FIG. 6A operates as follows. In the schematic of FIG. 6A, the inertial igniter 10 is shown in its pre-initiation state. Now if the device to which the inertial igniter is attached (for example a rocket or a missile) is accelerated in the direction of the arrow 15, if the acceleration is above the prescribed firing acceleration threshold, the inertial force due to the mass of the spring loading mass 11 is configured to overcome the preloading force of the tensile spring 16, and begin to move downward as viewed in FIG. 6A and as shown in FIG. 6B, causing the tip 34 of the spring loading mass 11 to come in contact with the surface 36 of the delay mechanism mass 28, and begin to push it back (to the left as seen in the view of FIG. 6B) and compress the spring 31.

If the prescribed acceleration persists, the spring loading mass 11 keeps moving down until its tip 34 clears the surface 36 of the delay mechanism mass 28 as shown in FIG. 6C, at which time the delay mechanism mass 28 has been pushed back and the spring 31 has been compressed their maximum amounts as shown in FIG. 6C. At this time, the compressively loaded spring 31 begins to accelerate the delay mechanism mass 28 to the right and its extended member 32 towards the tip 33 of the striker mass release member 22.

It is appreciated that if while the spring loading mass 11 is moving down and before releasing the delay mechanism mass 28 the acceleration threshold in the direction of the arrow 15 is ceased, the preloaded tensile spring 16 would bring the spring loading mass 11 to a stop and return it to its initial pre-acceleration and normal condition state.

Then at some point, the extended member 32 engages the tip 33 of the striker mass release member 22 and forces it to rotate in the clockwise direction as viewed in the schematic of FIG. 6D, which causes the tip 21 of the striker mass release member 22 to slide past the surface of the tip 20 of the striker mass member 17 as shown in FIG. 6D. The striker mass member 17 is thereby released and the preloaded compressive spring 19 begins to rotationally accelerate the striker mass member 17 in the clockwise direction. The preloaded compressive spring 19 is configured to accelerate the striker mass member 17 to the required kinetic energy for its ignition pin 26 to initiate the provided percussion primer 27 upon impact as shown by dashed lines in FIG. 6D. The generated ignition flame and sparks would then exit from the provided opening 38 to perform its intended function, for example to enter a thermal battery and activate the battery by igniting the battery pyrotechnic pallets.

It is appreciated by those skilled in the art that the delay mechanism mass 28 and the spring 31 assembly act as a vibrating mass-spring system with a natural frequency of

$\begin{array}{cc}\omega =\sqrt{\frac{k}{m}}& \left(1\right)\end{array}$ where k is the stiffness of the spring 31 and m is the mass of the delay mechanism mass 28, and ω (radian second) is the natural frequency of vibration of the mass-spring system. The period T of each cycle of vibration (oscillation) of the mass-spring system is then given as

$\begin{array}{cc}T=\frac{2\pi }{\omega }\mathrm{seconds}& \left(2\right)\end{array}$

It is also appreciated by those skilled in the art that the mass-spring system of delay mechanism mass 28 and the spring 31 is in its rest position in the schematic of FIG. 6A. The mass element 28 is then displaced to its position shown in the schematic of FIG. 6C by the spring loading mass 11, from which position it is released and starts it oscillatory motion. Thus, by the time that the delay mechanism mass 28 reaches its initially rest position of FIG. 6A, it has traveled one quarter of its cyclic motion, which would have taken a quarter of the period T, equation (2), i.e., a time duration of T/4 (seconds). The delay mechanism mass 28, however, passes its initially rest position of FIG. 6A as shown in the schematic of FIG. 6D before its extended member 32 would engage the tip 33 of the striker mass release member 22 and forces it to rotate in the clockwise direction as viewed in the schematic of FIG. 6D and thereby release the striker mass member 17. The delay mechanism mass 28, however, cannot travel a quarter of the cycle (to rest) in quarter of period T time since it needs enough kinetic energy to engage and force the striker mass release member 22 to rotate in the clockwise direction and release the striker mass member 17.

Thus, the total time t that it takes the delay mechanism mass 28 to release the striker mass member 17 by engaging and rotating the striker mass release member 22 can be greater than T/4 (seconds) but less than T/2 (seconds), i.e., T/2>t>T/4.

It is therefore appreciated that by varying the stiffness k of the spring 31 and mass m of the delay mechanism mass 28, the period T of the mass-spring system can be adjusted to match the required delay time from the detection of the aforementioned (setback in the case of fired munitions) acceleration threshold to the time of percussion primer initiation.

It is appreciated by those skilled in the art that once the inertial igniter embodiment 10 of FIG. 6A has detected the aforementioned prescribed acceleration threshold, i.e., once the spring loading mass 11 has overcome the preloading force of the tensile spring 16 and has completed spring 31 compression and has released the delay mechanism mass 28, the striker mass 17 is released after the above inertial igniter configured time t. This means that if the prescribed acceleration threshold persists less than the prescribed duration threshold, the striker mechanism would still initiate the percussion primer and thereby the reserve battery. In some munition applications, particularly in those with relatively short setback acceleration durations, this might not be an issue. However, in most munitions, particularly in rockets and missiles with relatively long setback duration threshold requirements, if the acceleration threshold is ceased before the prescribed duration threshold has elapsed, then the striker mass 17 must not be released to initiate the inertial igniter percussion primer or other provided pyrotechnic material and the inertial igniter must reset to its initial state shown in FIG. 6A. The following two modified inertial igniter embodiment of the embodiment 10 of FIG. 6A describe the methods of alleviating this shortcoming of the embodiment 10 the latter applications.

The schematic of the first modified inertial igniter embodiment 40 of the inertial igniter embodiment 10 of FIG. 6A is shown in FIG. 7A. All components of the inertial igniter embodiment 40 are identical to those of the embodiment 10, except for the extended member 32 of the delay mechanism mass 28, which instead of being fixedly attached to the delay mechanism mass, the “extended member” (indicated by the numeral 37 in FIG. 7A) is attached to the delay mechanism mass 28 by a rotary joint 38. In the normal conditions, the member 37 is held in the position shown in FIG. 7A by the preloaded tensile spring 39, which is attached to the delay mechanism mass 28 on one end 41 and to the member 37 on the other end as shown in FIG. 7A, preferably by pins that do not constrain their rotation.

Then as the device to which the inertial igniter embodiment 40 of FIG. 7A is attached is accelerated in the direction of the arrow 15, and while the spring loading mass 11 overcomes the preloading force of the tensile spring 16 and begins to compress the spring 31 to release the delay mechanism mass 28, the acceleration also acts on the mass of the member 37 and after overcoming the preloading force of the spring 39, begins to rotate the member 37 in the clockwise direction as viewed in FIG. 7A towards the provided stop 42. The preload level and stiffness of the spring 39 and the effective inertia of the member 37 are selected such that the member 37 is fully deployed and essentially held against the stop 42 as shown in FIG. 7B before the delay mechanism mass 28 is released as shown in FIG. 6D.

Now if the acceleration in the direction of the arrow 15 stays at or above the prescribed (all-fire in munitions) threshold, then the inertial igniter embodiment 40 functions as was described for the inertial igniter embodiment of FIG. 6A and at the indicated time t, the tip 43 of the member 37 would engage the tip 33 of the striker mass release member 22 and cause the striker mass 17 to be released and initiate the percussion primer 27 as shown in the schematic of FIG. 6D.

However, if at any time before the tip 43 of the member 37 engages the tip 33 of the striker mass release member 22 and releases the striker mass 17 the acceleration level in the direction of the arrow 15 drops below the prescribed threshold, the member 37 is rotated in the counterclockwise direction by the preloaded tensile spring 39 towards the configuration shown in FIG. 7A, thereby preventing the striker mass from being released and therefore the percussion primer 27 from being initiated. As a result, the modified inertial igniter embodiment 40 of FIG. 7A would only initiate the provided percussion primer or other pyrotechnic material 27 if the acceleration in the direction of the arrow 15 stays at or above the prescribed threshold and for the entire prescribed duration (all-fire condition in munitions).

It is appreciated that in the inertial igniter embodiment 40 of FIG. 7A the member 37 is shown to be deployed by rotation about a rotary joint 38, with which it is attached to the delay mechanism mass 28. Alternatively, the member 37 may instead be provided a guide (not shown) on the delay mechanism mass 28 to allow it to slide up and down in the direction parallel to the arrow 15, while being normally held up and away from engagement with the tip 33 of the striker mass release member 22 by a preloaded tensile spring like the spring 39. Then the member 37 would be similarly deployed by the acceleration in the direction of the arrow 15 when the acceleration is at or above the prescribed threshold for engagement with the tip 33 of the striker mass release member 22 and is withdrawn when the acceleration drops below the prescribed threshold to prevent engagement with the tip 33 of the striker mass release member 22.

In the second modified inertial igniter embodiment of the inertial igniter embodiment 10 of FIG. 6A, all components of the inertial igniter embodiment are identical to those of the embodiment 10, except for the striker mass release member 22, which is configured to avoid engagement with the extended member 32 of the delay mechanism mass 28 unless the inertial igniter is being subjected to acceleration in the direction of the arrow 15 that is at or above the prescribed (all-fire in munitions) threshold. In FIG. 8A, only the modified striker mass release member 44 (22 in FIG. 6A) together with the striker mass 17 mechanism components and the delay mechanism mass 28 and its components (shown in dashed lines) of the inertial igniter 10 are shown. The schematic of FIG. 8A shows the configuration of the striker mass release mechanism of the inertial igniter in normal conditions.

As can be seen in the schematic of FIG. 8A, as compared to the embodiment of FIG. 6A, the tip 33 of the striker mass release member 22 (44 in FIG. 8A) is lowered to below the extended member 32 of the delay mechanism mass 28, and is provided with the member 45, which is attached to the striker mass release member 44 by the rotary joint 46. In normal conditions shown in FIG. 8A, the member 45 is held in the configuration shown in FIG. 8A, i.e., under the extended member 32 of the delay mechanism mass 28 to prevent their engagement, by the compressive spring 47, which is attached to the member 45 on one end and to the striker mass release member 44 on the other end, preferably with pin joints that allow free rotation. In the normal condition configuration shown in FIG. 8A, the compressive spring 47 is essentially in its free length condition. Alternatively, an unloaded torsional spring (not shown) may be used instead of the compressive spring 47. In addition, the preloaded tensile spring 25 may also be replaced with a preloaded torsion spring (not shown) in all described embodiments. The preloaded tensile spring 25 may also be replaced by a preloaded compressive spring (48 in FIG. 8A) and positioned to bias the striker mass release member 44 against the stop 24 as shown in FIG. 8A.

Then as the device to which the inertial igniter embodiment with the components of FIG. 8A is attached is accelerated in the direction of the arrow 15 at or above the prescribed acceleration threshold, and while the spring loading mass 11 overcomes the preloading force of the tensile spring 16 and begins to compress the spring 31 to release the delay mechanism mass 28, FIG. 7A, the acceleration also acts on the mass of the member 45 with its mass center to the right of the rotary joint 46 as viewed in FIG. 8A, and after overcoming any present preloading force of the spring 47, begins to rotate the member 45 in the counterclockwise direction as viewed in FIG. 8A towards the provided stop 49. The stop 49 is fixedly attached to the striker mass release member 44. The preload level and the stiffness of the spring 47 and the effective inertia of the member 45 are selected such that the member 45 is fully deployed and essentially held against the stop 49 as shown in FIG. 8B before the delay mechanism mass 28 is released as shown in FIG. 6D.

Now if the acceleration in the direction of the arrow 15 stays at or above the prescribed (all-fire in munitions) threshold, then the inertial igniter embodiment 40 functions as was described for the inertial igniter embodiment of FIG. 6A and at the indicated time t, the extended member 32 of the delay mechanism mass 28 would engage the tip 51 of the striker mass release member 45 and cause the striker mass 17 to be released and initiate the percussion primer 27 as shown in the schematic of FIG. 6D.

However, if at any time before the extended member 32 of the delay mechanism mass 28 engages the tip 51 of the striker mass release member 45 and releases the striker mass 17 the acceleration level in the direction of the arrow 15 drops below the prescribed threshold, the member 45 is rotated in the clockwise direction by the tensile spring 47 towards the configuration shown in FIG. 8A, thereby preventing the striker mass 17 from being released and therefore the percussion primer 27 from being initiated. As a result, the modified inertial igniter embodiment 40 of FIG. 7A would only initiate the provided percussion primer or other pyrotechnic material 27 if the acceleration in the direction of the arrow 15 stays at or above the prescribed threshold and for the entire prescribed duration (all-fire condition in munitions).

It is appreciated by those skilled in the art that in the modifies inertial igniter embodiments of FIGS. 7A and 8A, if the acceleration in the direction of the arrow 15 is at or above the prescribed threshold but does not persist the entire prescribe duration, then the striker mass 17 is not released and the inertial igniter returns to its initial (normal) state, i.e., the inertial igniter is reset, and can later be initiated if the prescribed acceleration threshold and duration are detected.

The second inertial igniter embodiment 50 of the present invention is shown in the schematic of FIG. 9A. The inertial igniter 50 is similarly provided with a spring loading mass 52, which is free to translate in a guide (shown as the rolling members 53) along the surface 54 of the inertial igniter body 55 (shown as ground) in the direction parallel to the direction of firing acceleration indicated by the arrow 56. The spring loading mass 52 is provided with the preloaded tensile spring 57, which is attached to the inertial igniter body 55 on one end and to the spring loading mass 52 on the other end as shown in FIG. 9A.

The inertial igniter embodiment 50 of FIG. 9A is also provided with a striker mass member 58, which is attached to the inertial igniter body 55 by the rotary joint 59. The striker mass member 58 is also provided with a preloaded compressive spring 60, which biases it to keep its tip 61 against the tip 62 of the striker mass release member 63 as shown in FIG. 9A. The striker mass release member 63 is also attached to the inertial igniter body 55 by the rotary joint 64, and is provided with a preloaded tensile spring 66, which bias it against the stop 65 on the inertial igniter body 55 as shown in the configuration of FIG. 9A. The striker mass member 58 is also provided with a sharp tip 67, which is configured to initiate the percussion primer 68 (or other appropriate pyrotechnic material) upon impact as described later.

The inertial igniter embodiment 50 of FIG. 9A is also provided with a delay mechanism mass 69, which is free to translate in a guide (shown as the rolling members 70) along the surface 71 of the inertial igniter body 55 (shown as ground) in the direction perpendicular to the direction of firing acceleration indicated by the arrow 56. The delay mechanism mass 69 is provided with the spring 72, which is attached to the inertial igniter body 55 on one end and to the delay mechanism mass 69 on the other end as shown in FIG. 9A. In normal conditions shown in FIG. 9A, the spring 72 is in its free length (unloaded) condition. The delay mechanism mass 69 is also provided with the link member 73, which is attached to the delay mechanism mass 69 by the rotary joint 74. In normal conditions, the link member 73 is held against the stop 75 on the delay mechanism mass 69 by a very lightly preloaded and low spring rate (preferably torsional) spring (not shown for clarity). In the configuration shown in FIG. 9A, the tip 76 of the link member 73 is seen to be configured to engage the tip 77 of the striker mass release member 63 as the delay mechanism mass 69 travels to the right as viewed in FIG. 9A.

The inertial igniter embodiment 50 of FIG. 9A operates as follows. In the schematic of FIG. 9A, the inertial igniter 50 is shown in its pre-initiation state. Now if the device to which the inertial igniter is attached (for example a rocket or a missile) is accelerated in the direction of the arrow 56, if the acceleration is at or above the prescribed (all-fire) acceleration threshold, the inertial force due to the mass of the spring loading mass 52 is configured to overcome the preloading force of the tensile spring 57, and begin to move the spring loading mass 52 downward as viewed in FIG. 9A, causing the tip 78 of the spring loading mass 52 to come in contact with the surface 79 of the delay mechanism mass 69, and begin to push it back (to the left—as seen in the view of FIG. 6B for the embodiment 10 of FIG. 9A) and compress the spring 72.

If the prescribed acceleration persists, the spring loading mass 52 (shown in dashed lines) keeps moving down until its tip 78 clears the surface 79 of the delay mechanism mass 69 as shown in FIG. 9B, at which time the delay mechanism mass 69 has been pushed back and the spring 72 has been compressed their maximum amounts as shown in FIG. 9B. At this time, the compressively loaded spring 72 begins to accelerate the delay mechanism mass 69 to the right as viewed in FIG. 9B.

It is appreciated that if while the spring loading mass 52 is moving down and before releasing the delay mechanism mass 69 the acceleration threshold in the direction of the arrow 56 is ceased, the preloaded tensile spring 57 would bring the spring loading mass 52 to a stop and return it to its initial pre-acceleration and normal condition state.

Then as the delay mechanism mass 69 moves to the right as viewed in FIG. 9C, at some point, the tip 76 of the link member 73 engages the tip 77 of the striker mass release member 63, which would force the link member 73 to begin to rotate in the clockwise direction relative to the delay mechanism mass 69. The delay mechanism mass 69 will then continue translating to the right until it comes to a stop after reaching its maximum oscillation position as shown in FIG. 9D (essentially half the period of its aforementioned free oscillation period T, equation (2)), while at some point the tip 76 of the link member 73 clears the tip 77 of the striker mass release member 63.

The delay mechanism mass 69 will then begin to travel back to the left as viewed in FIG. 9E. Then at some point the tip 76 of the link member 73 engages the tip 77 of the striker mass release member 63 as shown in FIG. 9E. Then as the delay mechanism mass 69 translates further to the left, the tip 76 of the link member 73 (being prevented from rotating in the counterclockwise direction by the stop 75) begins to rotate the striker mass release member 63 in the counterclockwise direction as viewed in FIG. 9F, which causes the tip 62 of the striker mass release member 63 to slide passed the surface of the tip 61 of the striker mass member 58 as shown in FIG. 9F. The striker mass member 58 is thereby released and the preloaded compressive spring 60 begins to rotationally accelerate the striker mass member 58 in the counterclockwise direction. The preloaded compressive spring 60 is configured to accelerate the striker mass member 58 to the required kinetic energy for its ignition pin 67 to initiate the provided percussion primer 68 upon impact as shown by dashed lines in FIG. 9F. The generated ignition flame and sparks would then exit from the provided opening 82 to perform its intended function, for example to enter a thermal battery and activate the battery by igniting the battery pyrotechnic pallets.

It is appreciated by those skilled in the art that as was previously described for the inertial igniter embodiment 10 of FIG. 6A, the mass-spring system of delay mechanism mass 69 and the spring 72 is in its rest position in the schematic of FIG. 9A. The mass element 69 is then displaced to its position shown in the schematic of FIG. 9B by the spring loading mass 52, from which position it is released and starts it oscillatory motion. Thus, by the time that the delay mechanism mass 69 reaches its initial rest position of FIG. 9A, it has traveled one quarter of its cyclic motion, which would have taken a quarter of the period T, equation (2), i.e., a time duration of T/4 (seconds). It is noted that here we are neglecting energy losses due to friction and other effects, which are usually not considerable in low frequency oscillations and when the components, such as bearings and bearing surfaces are properly selected and configured.

The delay mechanism mass 28, would then passe its initial rest position of FIG. 6A as shown in the schematic of FIG. 6C and comes to rest after reaching its maximum oscillation position as shown in FIG. 9D, i.e., after traveling half of its full cyclic oscillatory motion from rest position of FIG. 9B to the rest position of FIG. 9D, for a duration of half the cycle period of T, equation (2).

The delay mechanism mass 69 will then begin to travel back to the left as viewed in FIG. 9E. Then at some point, preferably after passing the initial rest position of FIG. 6A, the tip 76 of the link member 73 engages the tip 77 of the striker mass release member 63 and rotates the striker mass release member 63 in the counterclockwise direction as viewed in FIG. 9F and releases the striker mass member 58 and initiate the percussion primer 68 as was previously described. It is therefore appreciated that the time elapsed as the delay mechanism mass 69 moves from its rest position of FIG. 9D to counterclockwise rotation of the striker mass release member 63 to release the striker mass member 58 would be more than a quarter but less than half the period T, equation (2), of the oscillation of the mass (69) and spring (72) system.

Thus, the total time t that it takes the delay mechanism mass 69 to release the striker mass member 58 by engaging and rotating the striker mass release member 63 can be greater than 3 T/4 (seconds) but less than T (seconds), i.e., T>t>3T/4.

It is therefore appreciated that by varying the stiffness k of the spring 72 and mass m of the delay mechanism mass 69, the period T, equation (2), of the mass-spring system can be adjusted to match the required delay time from the detection of the aforementioned (setback in the case of fired munitions) acceleration threshold to the time of percussion primer initiation.

It is also appreciated by those skilled in the art that for the same mass-spring sizes, the inertial igniter embodiment type 50 of FIG. 9A can provide more than almost twice the delay time as is possible with the inertial igniter embodiment type 10 of FIG. 6A. The inertial igniter embodiment type 50 of FIG. 9A are therefore more suitable for acceleration events with longer duration thresholds.

It is also appreciated by those skilled in the art that once the inertial igniter embodiment 50 of FIG. 9A has detected the aforementioned prescribed acceleration threshold, i.e., once the spring loading mass 52 has overcome the preloading force of the tensile spring 57 and has completed spring 72 compression and has released the delay mechanism mass 69 as shown in FIG. 9B, the striker mass 58 is released after the above inertial igniter configured time t. This means that if the prescribed acceleration threshold persists less than the prescribed duration threshold, the striker mechanism would still initiate the percussion primer and thereby the reserve battery. In some munition applications, particularly in those with relatively short setback acceleration durations, this might not be an issue. However, in most munitions, particularly in rockets and missiles with relatively long setback duration threshold requirements, if the acceleration threshold is ceased before the prescribed duration threshold has elapsed, then the striker mass 58 must not be released to initiate the inertial igniter percussion primer or other provided pyrotechnic material and the inertial igniter must reset to its initial state shown in FIG. 9A.

It is also appreciated by those skilled in the art that the two methods to modify the inertial igniter embodiment 10 of FIG. 6A as described for the embodiments of FIGS. 7A and 8A may also be used to modify the inertial igniter embodiment 50 of FIG. 9A to alleviate its above shortcoming as described below.

The schematic of the first modified inertial igniter embodiment 80 of the inertial igniter embodiment 50 of FIG. 9A is shown in FIG. 10. All components of the inertial igniter embodiment 80 are identical to those of the embodiment 50, except for the link member 73, which is replaced with the modified link member 83, which is similar to the link member 73. The link member 83 may be provided with a small side mass 84 to shift its center of mass slightly from the centerline of the link member for the reason described later. The link member 83 is also provided with the torsional spring 85, which in normal conditions is biased to keep the link member in the position shown in FIG. 10, i.e., horizontally as viewed in FIG. 10. The torsion spring is attached on one end to the link member 83 and to the delay mechanism mass 69 on the other end. A stop member (not shown) may also be provided on the delay mechanism mass 69 to prevent further clockwise rotation of the link member 83.

Then as the device to which the inertial igniter embodiment 80 of FIG. 10 is attached is subjected to an acceleration that is at or above the prescribed threshold in the direction of the arrow 56, and while the spring loading mass 52 overcomes the preloading force of the tensile spring 57 (both shown in dashed lines in FIG. 10) and compresses the spring 72 and releases the delay mechanism mass 69 as shown in FIG. 10, the acceleration also acts on the mass of the link member 84, and rotates it in the counterclockwise direction towards the stop 75 to the configuration shown with dashed lines and indicated by the numeral 86, while overcoming the force of the torsion spring 85. It is appreciated that as can be seen in the schematic of FIG. 10, the provision of the small mass 84 is intended to position the center of mass of the link member 83 to the right of the centerline of the link member as seen in its dashed lines configuration, thereby ensuring that the link member is positioned at or close to the stop 75 when the inertial igniter is subjected to the prescribed acceleration threshold. The torsion spring 85 rate and the effective inertia of the link member 83 in its positioning 86 are selected to provide minimal resistance to its clockwise rotation as it engages the tip 77 of the striker mass release member 63 as shown in the schematic of FIG. 9C.

Now if the acceleration in the direction of the arrow 56 stays at or above the prescribed (all-fire in munitions) threshold, then the inertial embodiment 80 functions as was described for the inertial igniter embodiment of FIG. 9A and at the indicated time t, the tip 87 of the member 83 (in its positioning 86) would engage the tip 77 of the striker mass release member 63 and cause the striker mass 58 to be released and initiate the percussion primer 68 as shown in the schematic of FIG. 9F.

However, if at any time before the tip 87 of the link member 83 engages the tip 77 of the striker mass release member 63 the acceleration level in the direction of the arrow 56 drops below the prescribed threshold, the link member 37 is rotated in the clockwise direction by the preloaded tensile spring 85 towards the configuration shown in solid line in FIG. 10, thereby preventing the striker mass from being released and therefore the percussion primer 68 from being initiated. As a result, the modified inertial igniter embodiment 80 of FIG. 10 would only initiate the percussion primer or other pyrotechnic material 68 if the acceleration in the direction of the arrow 56 stays at or above the prescribed threshold and for the entire prescribed duration t (all-fire condition in munitions).

It is appreciated that in the inertial igniter embodiment 80 of FIG. 10 the member 83 is shown to be deployed by rotation about a rotary joint 74 (FIG. 9A), with which it is attached to the delay mechanism mass 69. Alternatively, the link member 83 may instead be provided a guide (not shown) on the delay mechanism mass 69 to allow it to slide up and down in the direction parallel to the arrow 56, while being normally held up and away from engagement with the tip 77 of the striker mass release member 63 by a preloaded tensile spring like the spring 39 in FIG. 7A. Then the sliding link member 83 would be similarly deployed by the acceleration in the direction of the arrow 56 when the acceleration is at or above the prescribed threshold for engagement with the tip 77 of the striker mass release member 63 and is withdrawn when the acceleration drops below the prescribed threshold to prevent engagement with the tip 77 of the striker mass release member 63.

The schematic of the second modified inertial igniter embodiment 90 of the inertial igniter embodiment 50 of FIG. 10 is shown in FIG. 11. All components of the inertial igniter embodiment 90 are identical to those of the embodiment 50, except for the striker mass release member 63, which is replaced with the modified striker mass release member 88. The modified striker mass release member 88 is configured to avoid engagement with the tip 76 of the link member 73 of the delay mechanism mass 69 unless the inertial igniter is being subjected to an acceleration in the direction of the arrow 56 that is at or above the prescribed threshold (all-fire in munitions). In FIG. 11A, only the modified striker mass release member 88 (63 in FIG. 9A) together with the striker mass 58 mechanism components and the delay mechanism mass 69 and its components (shown in dashed lines) of the inertial igniter 50 (FIG. 9A) are shown. The schematic of FIG. 11A shows the configuration of the striker mass release mechanism of the inertial igniter in normal conditions.

The striker mass release member 63 (striker mass release member 88 in FIG. 11A) together with the striker mass 58 mechanism component of the inertial igniter 50, as shown in the enclosed dashed-lines area in FIG. 9B, is shown in the schematic of FIG. 11A. The schematic of FIG. 11A shows the configuration of the striker mass release mechanism of the inertial igniter in normal conditions.

As can be seen in the schematic of FIG. 11A, as compared to the embodiment of FIG. 9A, the tip 77 of the striker mass release member 63 (88 in FIG. 11A) is lowered to below the tip 76 of the link member 73 of the delay mechanism mass 69, and is provided with the member 89, which is attached to the striker mass release member 88 by the rotary joint 91. In normal conditions shown in FIG. 11A, the member 89 is held in the configuration shown in FIG. 11A, i.e., under the tip 76 of the link member 73 of the delay mechanism mass 69 to prevent their engagement, by the compressive spring 92, which is attached to the member 89 on one end and to the striker mass release member 88 on the other end, preferably with pin joints that allow free rotation. In the normal condition configuration shown in FIG. 11A, the compressive spring 92 is essentially in its free length condition. Alternatively, an unloaded torsional spring (not shown) may be used instead of the compressive spring 92. In addition, the preloaded compressive spring 94, which biases the striker mass release member 88 against the stop 95 may also be replaced with a preloaded torsion spring (not shown) in all described embodiments.

Then as the device to which the inertial igniter embodiment 90 with the components of FIG. 11A is attached is accelerated in the direction of the arrow 56 at or above the prescribed acceleration threshold (all-fire condition in munitions), and while as shown in FIG. 9A the spring loading mass 52 overcomes the preloading force of the tensile spring 57 and begins to compress the spring 72 to release the delay mechanism mass 69, FIG. 9B, the acceleration also acts on the mass of the member 89 with its center to the left of the rotary joint 91 as viewed in FIG. 11A, and after overcoming any present preloading force of the spring 92, begins to rotate the member 89 in the clockwise direction as viewed in FIG. 11A towards the provided stop 93. The preload level and the stiffness of the spring 92 and the effective inertia of the member 89 are selected such that the member 89 is fully deployed and essentially held against the stop 93 as shown in FIG. 11B as the delay mechanism mass 69 is released as shown in FIG. 9B.

Now if the acceleration in the direction of the arrow 56 stays at or above the prescribed (all-fire in munitions) threshold, then the inertial igniter embodiment 40 functions as was described for the inertial igniter embodiment of FIG. 9A and at the indicated time t, the tip 76 of the link member 73 of the delay mechanism mass 69 would engage the tip 96 of the striker mass release member 89, going through the stages shown in FIGS. 9C-9E, and cause the striker mass 58 to be released and initiate the percussion primer 68 as shown in the schematic of FIG. 9F.

However, if at any time before the tip 76 of the link member 73 of the delay mechanism mass 69 engages the tip 96 of the striker mass release member 89 on its return motion as shown in FIG. 9E to begin to rotate the striker mass release member 88 in the counterclockwise direction as viewed in FIG. 11B to release the striker mass 58 the acceleration level in the direction of the arrow 56 drops below the prescribed threshold, the member 89 is rotated in the clockwise direction by the compressive spring 92 towards the configuration shown in FIG. 11A. As a result, the striker mass 58 is not released and therefore the percussion primer 68 is not initiated. As a result, the modified inertial igniter embodiment 90 of FIG. 11A would only initiate the provided percussion primer or other pyrotechnic material 68 if the acceleration in the direction of the arrow 56 stays at or above the prescribed threshold and for the entire prescribed duration (all-fire condition in munitions).

It is appreciated by those skilled in the art that in the modifies inertial igniter embodiments of FIGS. 10 and 11A, if the acceleration in the direction of the arrow 56 is at or above the prescribed threshold but does not persist the entire prescribe duration, then the striker mass 58 is not released and the inertial igniter returns to its initial (normal) state, i.e., the inertial igniter is reset, and can later be initiated if the prescribed acceleration threshold and duration are detected.

It is appreciated by those skilled in the art that in the inertial igniter embodiment 80 of FIG. 10, once the link member 86 has passed to the right of the striker mass release member 63 as viewed in FIG. 10, if the acceleration in the direction of the arrow 56 drops below the prescribed threshold and if the tip 87 of the link member 86 is too close to the tip 77 of the striker mass release member 63, then the tip 87 of the link member 86 may not have enough room to clear the tip 77 of the striker mass release member 63 as it is rotated by the torsion spring in the clockwise direction relative to the delay mechanism mass 69. As a result, the releasing of the striker mass 58 is not prevented if the acceleration in the direction of the arrow 56 falls below the prescribed threshold as the link member 86 approaches the striker mass release member 63 for its actuation and is too close to it.

It is, however, also appreciated by those skilled in the art that the above shortcoming is not present in the inertial igniter embodiment 90 since as can be seen in FIG. 11B, the tip 96 of the member 89 is quickly removed from the path of the tip 76 of the link member 73 by the force of the spring 92 due to its short engagement tip length.

In the above inertial igniter embodiments, percussion primers are shown to be used to generate the required flame and sparks. It is appreciated that alternatively, appropriate pyrotechnic materials, such as those generally used in percussion primers or one of the recently developed green (no-lead) versions may be used directly as described for the prior art inertial igniters of FIGS. 1-5.

The above disclosed inertial igniter embodiments of the present invention are configured to initiate a percussion primer or some other appropriate pyrotechnic material when subjected to an acceleration that is at or above a prescribed threshold for a prescribed duration (all-fire condition for munitions). The basic operating mechanism of these embodiments may also be used to construct normally open (closed) electrical switches that close (open) a circuit when subjected to similar accelerations that are at or above a prescribed threshold for a prescribed duration (all-fire condition for munitions).

In the above disclosed inertial igniter embodiments, a striker mass member is released once an acceleration in the intended direction (direction of firing for munitions) that is at or above a prescribed threshold for a prescribed duration is detected, a striker mass is released and is accelerated to the required velocity by a preloaded spring (elastic) member to initiate a provided percussion primer or other pyrotechnic material upon impact. The same mechanism used for the release of the striker mass upon detection of the prescribed acceleration threshold and its duration can be used to provide the means of opening or closing or both of at least one electrical circuit, i.e., act as a so-called “Impulse Switch”, that is actuated only if it is subjected to the above prescribed minimum acceleration threshold for the prescribed minimum duration, while staying inactive during all other “impulse” conditions, even if the acceleration level is higher than the prescribed minimum acceleration threshold but its duration is shorter than the prescribed duration threshold.

Such “impulse switches” also have numerous non-munitions applications. For example, such impulse switches can be used to detect events such as impacts, falls, structural failure, explosions, etc., and open or close electrical circuits to initiate prescribed actions.

Such “impulse switch” embodiments for opening/closing electrical circuits, with and without latching features, are described herein together with alternative methods of their design, particularly as modular designs that can be readily assembled to the customer requirements.

The disclosed “impulse switches” function like the disclosed inertia igniter embodiments. They similarly comprise of two basic mechanisms so that together they provide for mechanical safety, and the switching mechanism, which provides the means to open or close electrical circuits. The function of the safety system is to prevent activation of the switching mechanism until the prescribed minimum acceleration threshold and its minimum duration has been detected and would only then releases the switching mechanism, thereby allowing it to undergo its actuation motion to open or close the electrical circuit by connecting or disconnecting electrical contacts. The switching mechanism may be held in its activated state, i.e., may be provided with a so-called latching mechanism, or may move back to its pre-activation state after opening or closing the circuit.

The basic design of such impulse switches using the design and functionalities of the disclosed inertial igniter embodiments is herein described using the inertial igniter embodiment of FIGS. 9A-9F. However, it is appreciated by those skilled in the art that other inertial igniter embodiments may also be similarly modified to function as impulse switches.

The schematic of such an impulse switch embodiment 100 is shown in FIG. 12. The basic design of the impulse switch 100 is the same as the inertial igniter embodiment 50 of FIGS. 9A-9F, except that its percussion primer 68 and the sharp pin 67 of the striker mass 58 are removed and replaced the electrical switching components and thereby converting the inertial igniter embodiment 50 into impulse switches for opening or closing electrical circuits as described below.

In the impulse switch embodiment 100 of FIG. 12, an element 101, which is constructed of an electrically non-conductive material is fixed to the impulse switch body 55. The electrically non-conductive element 101 may be attached to the impulse switch body 55 by fitting it into a provided pocket 102 in impulse switch body. The element 101 is provided with two electrically conductive elements 103 and 104 with contact ends 105 and 106, respectively. The electrically conductive elements 103 and 104 may be provided with the extended ends to form contact “pins” for direct insertion into provided holes in a circuit board or may alternatively be provided with wires 107 and 108, respectively, for connection to appropriate circuit junctions.

Previously described striker mass member 58 is provided with a flexible strip of electrically conductive material 109, FIG. 12, instead of the sharp pin 67, FIG. 9A. The flexible strip of electrically conductive material 109 is fixedly attached to the surface of the striker mass member 58 as shown in FIG. 12, for example, with fasteners 110 or by soldering or other methods known in the art.

The basic operation of the impulse switch 100 of FIG. 12 is very similar to that of the inertial igniter 50 of FIGS. 6A-6D. Here again and as was described for the inertial igniter 50, when the impulse switch 100 is accelerated in the direction of the arrow 56 at or above the prescribed threshold for the prescribed duration, the striker mass release member 63 is rotated in the counterclockwise direction until the striker mass member 58 is released as was described for the inertial igniter 50 and shown in FIG. 6D.

At this point, the mechanical (potential) energy in the preloaded compressive spring 60 begins to rotationally accelerate the striker mass 58 in the counterclockwise direction until the strip of the electrically conductive material 109 comes into contact with the contact ends 105 and 106, thereby closing the circuit to which the impulse switch 100 is connected through the electrically conductive elements 103 and 104 or wires 107 and 108 as shown in the schematic view of FIG. 14.

It is appreciated by those skilled in the art that the impulse switch 100 of FIGS. 12-13 is a “normally open impulse switch” and once activated due to the prescribed minimum acceleration level threshold in the direction of the arrow 56 for the prescribed duration, it would close the circuit to which it is connected as described above. The “normally open impulse switch” 100 may also be configured to be a “latching” type, i.e., keep the circuit closed after activation, or be a “non-latching” type, i.e., close the switch and momentarily open it.

To make the impulse switch 100 into a “latching normally open impulse switch” type, the level of preload in the compressive spring 60 is selected such that once the impulse switch is activated as shown in its activated state in the schematic of FIG. 13, the compressive spring 60 is still in its preloaded compressive state. As a result, following activation, as is seen in the schematic of FIG. 13, the electrically conductive material 109 strip is still forced against the contacts 105 and 106 by the still compressively preloaded spring 60.

However, to make the impulse switch 100 into a “non-latching normally open impulse switch” type, the level of preload in the compressive spring 60 is selected such that once the impulse switch is activated as shown in its activated state in the schematic view of FIG. 13, the compressive spring 60 has passed its free length (not loaded) state, i.e., it is loaded in tension, thereby moments after closing the circuit as shown in the schematic of FIG. 13, the striker mass 58 is rotated back in the clockwise direction as viewed in FIG. 13, and the contact between the electrically conductive material 109 strip and the contacts 105 and 106 is lost, thereby the circuit using the impulse switch 100 is open again.

The normally open impulse switch 100 of FIGS. 12-13 may also be modified to function as a normally closed impulse switch. The schematic of such a normally closed impulse switch embodiment 115 is shown in FIG. 14. The basic design and operation of the impulse switch 115 is identical to that of the normally open impulse switch embodiment 100 of FIGS. 12-13, except for its electrical switching contacts and related elements described below to convert it from a normally open to a normally closed impulse switch.

In the normally closed impulse switch embodiment 115 of FIG. 14, like the normally open impulse switch 100 of FIG. 12, an element 111, which is constructed of an electrically non-conductive material is fixed to the impulse switch body 55. The electrically non-conductive element 111 may be attached to the impulse switch body 55 by fitting it into a provided pocket (102 in FIG. 12) in the impulse switch body. The element 111 is provided with two electrically conductive elements 112 and 113 with flexible contact ends 116 and 117, respectively. The flexible electrically conductive contact ends 116 and 117 are biased to press against each other as seen in the schematic of FIG. 14. As a result, a circuit connected to the electrically conductive elements 112 and 113 is normally closed in the pre-activation state of the impulse switch 115 as shown in the configuration of FIG. 14.

The electrically conductive elements 112 and 113 may be provided with the extended ends to form contact “pins” for direct insertion into provided holes in a circuit board or may alternatively be provided with wires 118 and 119, respectively, for connection to appropriate circuit junctions.

Previously described striker mass member 58 is provided with an electrically nonconductive wedge element 114, which is fixed to the surface of the striker mass member 58 as shown in FIG. 14, for example, by an adhesive or using other methods known in the art.

The basic operation of the impulse switch 115 of FIG. 14 is very similar to that of the inertial igniter 50 of FIGS. 6A-6D. Here again and as was described for the inertial igniter 50, when the impulse switch 115 is accelerated in the direction of the arrow 56 at or above the prescribed threshold for the prescribed duration, the striker mass release member 63 is rotated in the counterclockwise direction until the striker mass member 58 is released as was described for the inertial igniter 50 and shown in FIG. 6D.

At this point, the mechanical (potential) energy in the preloaded compressive spring 60 begins to rotationally accelerate the striker mass 58 in the counterclockwise direction until the electrically nonconductive wedge element 114 is inserted between the contacting surfaces of the flexible electrically conductive contact ends 116 and 117, thereby opening the circuit to which the impulse switch 115 is connected (through the electrically conductive elements 112 and 113 or wires 118 and 119) as shown in the schematic view of FIG. 15.

It is appreciated by those skilled in the art that the impulse switch 115 of FIGS. 14-15 is a “normally closed impulse switch” and once activated due to the prescribed minimum acceleration level threshold in the direction of the arrow 56 for the prescribed duration, it would open the circuit to which it is connected as described above. The “normally closed impulse switch” 115 may also be configured to be a “latching” type, i.e., keep the circuit open after activation, or be a “non-latching” type, i.e., open the switch and momentarily close as described below.

To make the impulse switch 115 into a “latching normally closed impulse switch” type, the level of preload in the compressive spring 60 is selected such that once the impulse switch is activated as shown in its activated state in the schematic of FIG. 15, the compressive spring 60 is still in its preloaded compressive state. As a result, following activation, as is seen in the schematic of FIG. 15, the electrically nonconductive wedge element 114 would thereby stay inserted between the contacting surfaces of the flexible electrically conductive contact ends 116 and 117 and the circuit stays open.

However, to make the impulse switch 115 into a “non-latching normally closed impulse switch” type, the level of preload in the compressive spring 60 is selected such that once the impulse switch is activated as shown in its activated state in the schematic view of FIG. 15, the compressive spring 60 has passed its free length (not loaded) state, i.e., it is loaded in tension, thereby moments after closing the circuit as shown in the schematic of FIG. 15, the striker mass 58 is rotated back in the clockwise direction as viewed in FIG. 15, and the flexible electrically conductive contact ends 116 and 117 come into contact and the impulse switch is closed again.

The embodiments 100 and 115 of FIGS. 12-13 and 14-15, respectively, illustrate how the inertial igniter embodiment 50 of FIGS. 9A-9F can be converted to normally open and normally closed electrical “impulse switches” of latching and non-latching types. It is appreciated by those skilled in the art that the inertial igniters of FIGS. 6A-6D, 7A-7B, 8A-8B, 10 and 11A-11B may also be similarly converted to any of the above electrical “impulse switch” types.

It is appreciated by those skilled in the art that in thermal and other reserve batteries that use inertial igniters, particularly if the inertial igniter is assembled inside the battery housing or inside the device housing, it is highly desirable to have the capability of determining if the initiator has been activated or not, for example after an accidental drop. In certain cases, the inertial igniter has activated but the reserve battery has failed to activate. In yet another case, the inertial igniter may have been activated but the percussion primer or other pyrotechnic material that is used may have not been ignited. In short, it is highly desirable for the reserve battery user to be able to determine the status of the battery without having to perform x-ray or other complicated and expensive testing. In addition, in certain applications, it is highly desirable for the munitions and/or the weapon system control system to be able to obtain the above battery status information for optimal operation and safety. To this end, the disclosed inertial igniter embodiments may be readily equipped to perform the above tasks as described below by an example of the required modifications to the embodiment 50 of FIGS. 6A-6D. The remaining embodiments may be similarly modified to perform the described functionality.

FIG. 16 shows the schematic view of the embodiment 50 just as the striker mass 58 is released as shown in FIG. 9F, with the modification for the inertial igniter to also function as an electrical switch, which would indicate if the inertial igniter has been activated, i.e., for the user to determine the activation state of the inertial igniter. The resulting inertial igniter with the integrated “activation state indicating sensor” of FIG. 16 is indicated by the numeral 120 and is hereinafter referred to as the “inertial igniter with activation sensor”.

The “inertial igniter with activation state indicating sensor” embodiment 120 of FIG. 16 is identical to the inertial igniter embodiment 50 of FIGS. 6A-6D, except for the addition of the following electrical contact forming components to provide the means of sensing whether the inertial igniter has been activated. In the “inertial igniter with activation state indicating sensor” embodiment 120, like the impulse switch embodiment 100 of FIG. 12, an element 121 (101 in FIG. 12), which is constructed of an electrically non-conductive material is fixed to the body 55 (shown as ground) of the inertial igniter. The electrically non-conductive element 121 may be attached to the body 55 of the inertial igniter by fitting it in the matching opening as shown in FIG. 16. The element 121 is provided with two electrically conductive elements 122 and 123 with contacts 124 and 125, respectively. The electrically conductive elements 122 and 123 may be extended to form contact “pins” for direct insertion into provided holes in a circuit board or may alternatively be provided with wires 126 and 127 for connection to appropriate circuit junctions.

Previously described striker mass 58 is then provided with a flexible strip of electrically conductive material 128, which is fixed to the surface of the striker mass 58 as shown in FIG. 16, for example, with fasteners 129 or by soldering or other methods known in the art.

The operation of the “inertial igniter with activation state indicating sensor” embodiment 120 of FIG. 16 is the same as that of the inertial igniter 50 of FIGS. 6A-6D. Here again and as was described for the inertial igniter 50, when the “inertial igniter with activation state indicating sensor” embodiment 120 is accelerated in the direction of the arrow 56 at or above the prescribed threshold and for the prescribed duration (all-fire condition in munitions), the striker mass release member 63 is rotated in the counterclockwise direction until the striker mass member 58 is released and is rotationally accelerated in the counterclockwise direction until the sharp tip 67 of the striker mass member 58 strikes the percussion primer or other appropriate pyrotechnic material 68 and initiates it as shown in FIG. 6D. In the meantime, the strip of the electrically conductive material 128 would come into contact with the contact ends 124 and 125, thereby closing the circuit to which the electrically conductive elements 122 and 123 (or their connected wires 126 and 127) are connected, indicating that the “inertial igniter with activation state indicating sensor” has been activated.

Alternatively, since the striker mass member 58 is usually metallic, for example made from brass or stainless steel and therefore electrically conductive, there may not be any need for the flexible strip of electrically conductive material 128. In such cases, the contact ends 124 and 125 may be flexible to ensure contact with the surface of the striker mass member 58.

The “inertial igniter with activation state indicating sensor” embodiment 120 is shown to perform percussion primer initiation as well as an impulse switch functionality. As a result, when the device is packaged in a reserve battery or in any other device for initiation of pyrotechnic materials or the like, the user or the system controller or diagnostic system can check the activation status of the inertial igniter for safety and/or for system readiness or the like. The activation status sensor component of the device may also be used as an input to the system activation status indication algorithm, for example as an independent sensory input to munitions fuzing to indicate if the munitions was fired.

The “inertial igniter with activation state indicating sensor” embodiment 120 acts as a normally open and latching electrical impulse switch, in which the switch is closed and stays closed when the inertial igniter is activated. It is appreciated by those skilled in the art that the electrical impulse switch may also be configured to be of a non-latching type. Similarly, the electrical impulse switch may also be configured as a normally closed electrical impulse switch of latching and non-latching type as was described for the impulse switch embodiment of FIGS. 12-15.

The disclosed inertial igniter embodiments of FIGS. 6A-6D, 7A-7B, 8A-8B, 9A-9F, 10 and 11A-111B; the electrical switch embodiments of FIGS. 12-15, and the “inertial igniter with activation state indicating sensor” embodiment of FIG. 16 are all configured with a linearly oscillating mass-spring mechanisms (delay mechanism mass 69 and spring 72 for the case of the inertial igniter 50 of FIGS. 9A-9F).

In certain applications, such as in many gun-fired munitions, rockets, and missiles, besides the setback acceleration, munitions are also subjected to considerable lateral acceleration pulses (usually called balloting in munitions). In such applications, as can, for example, be seen in the schematic of FIG. 9A, the inertial igniter embodiment 50 may be subjected to acceleration/deceleration pulses in the directions perpendicular to the direction of the firing indicated by the arrow 56. It is appreciated by those skilled in the art that such acceleration/deceleration pulses, even though they are always very short in duration and do not result in a net displacement of the munition inside the barrel or the like, can have a net effect on the previously described prescribed duration t of the prescribed (firing) acceleration threshold.

It is also appreciated by those skilled in the art that in certain munitions applications, the munitions are subjected to significant spin accelerations as well as setback acceleration during launch. In addition, while the inertial igniter is in the process of initiating its percussion primer, i.e., during the previously indicated duration t of the prescribed (firing setback in munitions) acceleration threshold, the munition may have gained a considerable spin velocity. It is appreciated that as can be observed, for example in the schematic of FIG. 9A, since the delay mechanism mass 69 displaces laterally relative to the spin axis of the munition to which it is attached (which is parallel to the direction of acceleration shown by the arrow 56), therefore the delay mechanism mass 69 would be subjected to a varying centrifugal force, which would affect its oscillation period T, equation (2), thereby the intended duration t that the inertial igniter is to be subjected to the prescribed (setback) acceleration threshold to release the inertial igniter striker mass member 58.

It is appreciated that for such applications, the inertial igniter (and the related electrical impulse switches) must be configured to be essentially insensitive to lateral and spin accelerations and spin velocity.

It is also appreciated by those skilled in the art that the effect of such short lateral acceleration and deceleration pulses with no net displacement is generally negligible when the previously indicated duration t of the prescribed (firing setback in munitions) acceleration threshold is long as compared to the duration of the lateral acceleration and deceleration pulses, for example, tens of milliseconds of duration t for the prescribed acceleration threshold as compare to tens of microseconds for the lateral acceleration and deceleration pulses.

In applications in which the effect of lateral acceleration and deceleration pulses and/or spin acceleration and/or spin rate during the inertial igniter initiation process as a result of the applied prescribed acceleration threshold for the prescribed duration is not negligible, then the inertial igniter mechanisms must be configured such that they are not sensitive to the said effects and can reliably operate in such environments.

It is appreciated that can be seen in the above inertial igniter embodiments of the present invention; the inertial igniters are constructed by the following two relatively independently operating mechanisms.

The first mechanism, referred to as the mechanical delay mechanism, is configured to actuate certain member, in this case a member that would release the inertial igniter striker mass when the mechanical delay mechanism is subjected to the prescribed acceleration threshold (firing setback acceleration for munitions) that persists for the prescribed duration (all-fire condition for munitions), and resetting to its initial configuration if the prescribed acceleration threshold and/or its prescribed duration conditions are not met. For example, in the inertial igniter embodiment 50 of FIG. 9A, the assembly of the mass member 69 with the link 73 and the spring 72 and the actuating mass 52 and its spring member 57 provide the mechanical delay mechanism for this inertial igniter embodiment.

The second mechanism, referred to as the striker mechanism, consists of a mass element with a preloaded spring (elastic) element (for example, striker mass 58 and preloaded compression spring 60 in the embodiment 50 of FIG. 9A) with the required amount of stored potential energy to accelerate the striker mass to the required velocity to achieve reliable percussion cap or pyrotechnic material initiation upon impact. The striker mass is provided with a release mechanism (member striker mass release member 63 in the embodiment 50 of FIG. 9A), which is actuated by the mechanical delay mechanism upon detection of the prescribed acceleration threshold and its duration condition.

In the following embodiments of the present invention, mechanical delay mechanism designs are provided that are insensitive to the previously described lateral acceleration and deceleration pulses, spin accelerations and spin velocity. It is appreciated that the spin is intended to indicate rotation about the direction of acceleration that is to be detected by the inertial igniter for initiation (direction of the firing acceleration in munitions) and lateral directions are normal to the said direction of acceleration.

FIG. 17 shows the top view (the direction of acceleration that is to be detected by the inertial igniter for initiation being perpendicular to the view of FIG. 17 and outward) of the mechanical delay mechanism embodiment 130, which is configured to be insensitive to the aforementioned lateral and spin accelerations and spin velocity. The frontal view “A”, FIG. 17, of the mechanical delay mechanism 130 is shown in the schematic of FIG. 18A.

As can be seen in the schematic of FIG. 17, the mechanical delay mechanism embodiment 130 of the inertial igniter consists of a wheel 131, which is fixedly attached to the shaft 132, which is free to rotate in the bearing 145 that is provided in the body of the inertial igniter 133 (shown as ground). Fixedly also attached to the shaft 132 is the gear 134, which is engaged with the pinion 135. The pinion 135 is fixedly attached to the shaft 136, which is free to rotate in the bearing 146 that is provided in the body of the inertial igniter 133. A wheel 137 is also fixedly attached to the shaft 136 as can be seen in the schematic of FIG. 17. A provided torsion spring 138 is connected on one end to the shaft 136 and on the other end 139 to the body of the inertial igniter 133.

The mechanical delay mechanism embodiment 130 is also provided with a link member 140, FIGS. 17 and 18A, which is fixedly attached to the shaft 141, which is free to rotate in the bearing 147 that is provided in the body of the inertial igniter 133. A mass member 144 is provided on the link 140, which in practice would be integral to the link 140 structure, to shift the center of mass of the link 140 towards the wheel 131.

The frontal view “A” of FIG. 17 is shown in FIG. 18A. In the schematic of FIG. 17 and the front view 18A, the mechanical delay mechanism embodiment 130 is shown in its normal conditions, i.e., in the configuration before the inertial igniter being subjected to the previously described prescribed activation acceleration profile.

In the frontal view “A” of FIG. 18A, the pinion 135 and its connected components are not shown. As can be seen, the wheel 131 is provided with symmetric cuts with sides 149 and 150. The reason for providing such symmetric cuts is to ensure that the center of mass of the wheel 131 is located at the center of the shaft 132. The link member 140 is also provided with a slightly preloaded tensile spring 148 to bias the link against the stop 152, which is provided on the body 133 of the mechanical delay mechanism 130. In the normal configuration of the mechanical delay mechanism, the tensile spring 148 is preloaded to keep the link member against the stop 152 and its tip 142 over the surface 150 of the cut in the wheel 131 as shown in FIG. 18A. The tensile spring 148 is usually preloaded such that the acceleration in the direction of the arrow 151 of a few G (e.g., 2-3 G for a prescribed acceleration threshold of 20-30 G), would not generate enough downward force due to the mass member 144 and off-center mass of the link member 140 to rotate the link member in the clockwise direction as viewed in FIG. 18A.

In the schematic of FIG. 18A, the preloaded tensile spring 148 is used to bias the link 140 against the stop 152 and prevent its rotation for relatively low G accelerations in the direction of the arrow 151. It is appreciated that a similarly preloaded compressive spring may also be used and positioned on the opposite side of the link 140 to perform the same function. It is also appreciated that a preloaded torsion spring (not shown), positioned over the shaft 141 of the link 140, one end of which being attached to the mechanical delay mechanism body 133 and the other end being attached to the link 140 (similar to the torsion spring 138, FIG. 17) may also be used instead of the preloaded tensile spring 148.

The mechanical delay mechanism 130 of FIGS. 17 and 18A operates as follows. In normal conditions, the link 140 is held in the position shown in FIG. 18A by the preloaded tensile spring 148 and its tip 142 is over the edge 150 of the provided cut in the wheel 131 as can be seen in FIG. 18A. The wheel 131 is also held in the position shown in FIG. 18A by the torsion spring 138 via the gear 134 and pinion 135, in which position, the torsion spring is in its free unloaded configuration.

Then when the device to which the inertial igniter using the mechanical delay mechanism of FIG. 17 is attached is accelerated in the direction of the arrow 151, FIG. 18A, if the acceleration is high enough to overcome the tensile spring 148 preload, then the downward force due to the mass member 144 and the link 140 would result in a clockwise torque that tends to rotate the link 140 in the clockwise direction. Then as the link 140 begins to rotate in the clockwise direction, its tip 142 begins to apply a downward force as viewed in the schematic of FIG. 18A, which would tend to rotate the wheel 131 in the counterclockwise direction. The counterclockwise rotation of the wheel 131 is then transmitted to the pinion 135, rotating the shaft 136 an increased amount indicated by the ratio of the number of teeth on the gear 134 and the number of teeth on the pinion 135. The rotation of the shaft 136 will then results in winding of the torsion spring 138 and storing mechanical potential energy in the torsion spring.

Now if the acceleration in the direction of the arrow 151 continues and stays above the previously described prescribed threshold (all-fire acceleration level in munitions), then the link 140 will keep rotating in the clockwise direction, thereby keep on rotating the wheel 131 in the counterclockwise direction as shown in FIG. 18B, thereby further winding the torsion spring 138 and storing more mechanical potential energy in the torsion spring 138.

Now if the acceleration in the direction of the arrow 151 continues and stays above the previously described prescribed threshold (all-fire condition in munitions) long enough, then the link 140 will keep rotating in the clockwise direction and thereby rotating the wheel 131 in the counterclockwise direction until its tip 154 clears the tip 155 of the edge 150 of the cut in the wheel 131 as shown in the schematic of FIG. 18C. Otherwise, the tension spring 148 and the torsion spring 138 would force the link 140 and wheel 131 to return to their initial positioning of FIG. 18A.

Then if the acceleration in the direction of the arrow 151 continues and stays above the previously described prescribed threshold, the link 140 will stay down against the stop 153 as shown in FIG. 18C and the wheels 131 and 137 as coupled with the gear 134 and pinion 135 with their equivalent moment of inertia I_eq and the torsion spring 138, forming a torsional vibration system, would undergo its oscillatory rotations.

It is appreciated by those skilled in the art that at the time of disengagement between the tip 154 of the link 140 and the tip 155 of the wheel 131, FIG. 18C, the wheel 131 has gained some rotational velocity and would therefore continue to rotate in the counterclockwise direction until the corresponding kinetic energy stored in the equivalent moment of inertia I_eq of the mechanical delay mechanism has been converted to mechanical potential energy that is stored in the torsion spring 138. It is also appreciated that here and in the following descriptions of the operation of the mechanical delay mechanism embodiment 130 of FIG. 17 and for the sake of simplicity, the mechanical energy losses due to friction and other sources are going to be neglected.

During this oscillatory motion, assuming that the wheel 131 has come to a stop from its counterclockwise rotation in the position shown in FIG. 18C, the wheel 131 is accelerated rotationally in the clockwise direction as viewed in FIG. 18C until the torsion spring has transferred its entire stored mechanical potential energy to the wheels 131 and 137 assembly as mechanical kinetic energy, which neglecting friction and other losses, would take one quarter of the period of oscillation of the present oscillatory motion. At this point, the wheel 131 has reached its maximum clockwise rotational velocity. From this point on, the clockwise rotation of the wheel 131 is decelerated while the mechanical kinetic energy stored in the wheels 131 and 137 assembly is returned to the torsion spring 138 as mechanical potential energy, ending half the period of the system oscillatory motion, at which time the wheel 131 comes to a stop. The wheel 131 will then begin to rotate in the counterclockwise direction, similarly, reach its maximum rotational velocity after a quarter of the period of the system oscillation and comes to a stop at its initial position of FIG. 18C after completing one full cycle of the torsional system oscillation, during the corresponding period of the oscillatory motion.

It is appreciated by those skilled in the art that as is described above, as the wheel 131 is released as shown in the schematic of FIG. 18C, it starts rotating in the clockwise direction, passes its initial stationary position shown in FIG. 18A, and neglecting friction and other losses, would further rotate in the clockwise direction the same amount as shown in FIG. 18D, completing half of its cycle of oscillation in half the period of its oscillatory motion. Now as the wheel 131 is rotating in the clockwise direction, at some point the outward protruding member 160 (shown only in the schematic of FIG. 18D) engages the tip 159 of the link 157 and rotates it in the counterclockwise direction to the position shown by dashed lines and indicated by the numeral 156.

The link 157 is attached to the body 133 of the inertial igniter that is using the present mechanical delay mechanism 130 by the rotary joint 158. The link 157 is also provided with a preloaded torsion spring (not shown) at the joint 158, one end of which is attached to the link 157 and the other to the device body 133 and is used to keep the link 157 biased against the stop 162.

It is appreciated by those skilled in the art that the wheels 131 and 137 together with their geared transmission with an equivalent moment of inertial I_eq together with the torsion spring 138, with spring constant k_T, form a mass-spring torsional vibration system vibrating at a natural frequency of

$\begin{array}{cc}\omega =\sqrt{\frac{k_T}{I_{\mathrm{eq}}}}& \left(3\right)\end{array}$ where ω (radian second) is the natural frequency of vibration of the torsional vibration system. The period T of each cycle of vibration (oscillation) of the torsional vibration system is then given as

$\begin{array}{cc}T=\frac{2\pi }{\omega }\mathrm{seconds}& \left(4\right)\end{array}$

It is appreciated by those skilled in the art that as can be seen in the schematic of FIG. 18D, which is shown after to torsional vibration system has gone through half of its cycle of oscillation, i.e., at half its period of oscillation T, equation (4), from the point at which the wheel 131 has come to a stop following its release, FIG. 18C. Now as can be seen in FIG. 18D, the link 157 is rotated to its position 156 before the wheel reaching its position of FIG. 18D, i.e., before half the period of oscillation T has elapsed, therefore it is concluded that from the time that the wheel 131 has come to a stop following its release, FIG. 18C, to the time of full rotation of the link 157, the total time t that has elapsed is t<T/2.

It is appreciated by those skilled in the art that the lever 157 can be used in any inertial igniter with preloaded spring (elastic element) striker mechanism for its release and initiation of the provided percussion primer or other provided pyrotechnic material, such as to serve as the striker mass release member 63 in the inertial igniter 50 of FIG. 9A, for releasing the striker mass 58 to ignite the percussion primer 68.

It is also appreciated by those skilled in the art that the method used in the inertial igniter 50 of FIG. 9A to increase the delay mechanism time t above half period T of oscillation of the torsional vibration system may also be used with the mechanical delay mechanism 130 of FIG. 17 by modifying the lever 157, FIG. 18D. Such a modified design of the lever 157 together with the mechanical delay mechanism 130 of FIG. 17 is shown in the schematic of FIG. 18E.

In the modified release link design of FIG. 18E, the release link 163 (157 in FIG. 18D) is similarly attached to the body 133 of the inertial igniter that is using the present mechanical delay mechanism 130 by the rotary joint 164. The link 163 is also provided with a preloaded torsion spring (not shown) at the joint 164, one end of which is attached to the link 163 and the other to the device body 133 and is used to keep the link 163 biased against the stop 165.

The release link 163 is also provided with an engagement link 166, which is attached to the link 163 by the rotary joint 167. The engagement link 166 is free to rotate relative to the release link 163 but is provided with a lightly preloaded torsion spring (not shown) at the joint 167, one end of which is attached to the link 163 and the other to the engagement link 166 and is used to keep the link 166 biased against the stop 168, which is fixedly attached to the release link 163.

It is appreciated by those skilled in the art that as it was previously described, as the wheel 131 is released as shown in the schematic of FIG. 18C, it starts rotating in the clockwise direction, passes its initial stationary position shown in FIG. 18A, and neglecting friction and other losses, would further rotate in the clockwise direction the same amount as shown in FIG. 18D, completing half of its cycle of oscillation in half the period of its oscillatory motion. Now as the wheel 131 is rotating in the clockwise direction, as shown in FIG. 18E, at some point the outward protruding member 160 (shown only in the schematic of FIGS. 18D and 18E) engages the tip 169 of the engagement link 166 and begins to rotate it in the counterclockwise direction relative to the release link 163. It is appreciated that since the link 163 is prevented from rotating in the counterclockwise direction by the stop 165, the engagement link 166 is rotated in the counterclockwise direction relative to the release link 163 until it is rotated out of the path of the outward protruding member 160 as shown by the dashed lines and indicated by the numeral 170. The aforementioned provided lightly preloaded torsion spring (not shown) at the joint 167 would then return the engagement link 166 to its positioning against the stop 168 and the wheel 131 would continue to rotate in the clockwise direction until it is brought to a stop by the winding torsion spring 138, FIGS. 18E and 17, at which time half the period T of oscillation of the torsional vibration system has elapsed.

The wheel 131 will then begin to rotate in the counterclockwise direction by the torsion spring 138 until the outward protruding member 160 engages the lower section of the tip 169 of the engagement link 169 (as viewed in FIG. 18E), and begin to rotate the release link 163 in the clockwise direction and cause the release of an engaging striker mechanism as was described for the mechanism of FIG. 18D, once the release link 163 is rotated the required amount, such as shown by the dashed lines and indicated by the numeral 171. In general, the inertial igniter is configured such that after the release link 163 is rotated some amount further, the outward protruding member 160 is disengages the tip 169 of the engagement link 166 and continue its counterclockwise rotation.

It is appreciated that the aforementioned total time t that has elapsed, i.e., the delay time t, from the time of wheel 131 release shown in FIG. 18C to the time of clockwise rotation of the striker release link 163 become larger than half the period of oscillation T, i.e., the total delay time becomes t>T/2.

Now as can be seen in FIG. 18E, the link 157 is rotated to its position 156 before the wheel reaching its position of FIG. 18D, i.e., before half the period of oscillation T has elapsed, therefore it is concluded that from the time that the wheel 131 has come to a stop following its release, FIG. 18C, to the time of full rotation of the link 157, the total time t that has elapsed is t<T/2.

It is also appreciated that if the duration of acceleration in the direction of the arrow 151 is short, then the preloaded spring 148 would return the link 140 to its normal condition shown in FIG. 18A.

It is appreciated by those skilled in the art that many munitions are subjected to high spin rates during the firing (in the direction of the arrow 151, FIG. 18A) and for that reason, the mechanical delay mechanism of FIG. 17 is suitable for the design of such inertial igniters since their operation is not affected by spin acceleration and spin velocity.

In addition, since the center of mass of the wheels 131 and 137 and the gears 134 and 135 lies on the axes of rotation of the shafts 132 and 136, and by ensuring that the center of mass of the link 140 and mass 144 also lies in a plane perpendicular to the direction of the arrow 151 and containing the axis of rotation of the joint 141, then any lateral shock loading of the mechanical delay mechanism 130 of FIG. 17 would not cause in counterclockwise rotation of the wheel 131. Therefore, the mechanical delay mechanism 130 can be used in the design of inertial igniters that can withstand high G lateral shock loadings and high spin acceleration and spin rates.

Another inertial igniter embodiment 400 that is insensitive to the previously described lateral acceleration and deceleration pulses, spin accelerations and spin velocity, which is configured using the above methods and is intended to be easier to manufacture and assemble is shown in the top view schematic of FIG. 19. It is appreciated that as it was previously described, the spin is intended to indicate rotation about the direction of acceleration that is to be detected by the inertial igniter for initiation (direction of the firing acceleration in munitions) and lateral directions are normal to the direction of acceleration. It is also appreciated that in the view of the schematic of FIG. 19, the activation acceleration is considered to be perpendicular to the plane of view and pointing out of the plane of the view.

The inertial igniter embodiment 400 of FIG. 19 comprises an inertially actuated “spring winding component”, which is enclosed by the indicated dashed-line rectangle 401, which drives the delay mechanism of the inertial igniter as is described later, and the initiator striker mechanism component, FIG. 26, which is powered by a preloaded spring, the position of which is indicated by the dashed-lines square 402 (the components of the striker mechanism are not shown in FIG. 19 for the sake of clarity).

The top view of the inertially actuated “spring winding component” 401 of the inertial igniter embodiment 400 of FIG. 19 is shown in the schematic of FIG. 20A. The inertially actuated “spring winding component” 401 comprises the shaft 403, which is free to rotate in the bearings 404 and 405, which are provided in the structure 406 of the inertial igniter embodiment 400 of FIG. 19. Attached to the shaft 403, are then at least one link member 407 which is attached to the shaft by a bearing, preferably a ball bearing, which allows it to freely rotate about the shaft 403. In the schematic of FIG. 20A, two other similar levers 408 and 409 are also shown, which are also similarly attached to the shaft 403 and are free to rotate about the shaft.

The cross-sectional view C-C of FIG. 20A is shown in FIG. 20B, showing the side view of the first inertially actuating link member 407 of the inertial spring winding component of the inertial igniter embodiment of FIG. 19. As indicated above, the link member 407 is attached to the shaft 403 by the bearing 416 and is free to rotate over the shaft within the range described below. As can be seen in FIG. 20B, the shaft 403 is provided with a pin 411, which is positioned in the groove 412 that is provided in the body of the link member 407 to accommodate it. In the position shown in FIG. 20B, the pin 411 is resting against the stop member 413, which is provided inside the groove 412. A mass member 410 is also attached to the free side of the link member 407 as shown in FIG. 20B.

In normal conditions, a preloaded torsion spring 415 (not shown in FIG. 20B), FIG. 20A, applies a counterclockwise torque to the link member 407 as viewed in the cross-sectional view of FIG. 20B, which biases the link member 407 against the stop 417, which is provided on the structure 406 of the inertial igniter embodiment 400. The preloaded torsion spring 415 is attached to the link member 407 on one end and to the structure 406 of the inertial igniter embodiment 400 on the other end. It is noted that the stop 417 is not shown in the schematics of FIGS. 19 and 20A for the sake of clarity. Similar stop members are also provided for the link members 408 and 409 in their normal positionings shown in FIG. 20A and are also not shown for the sake of view clarity.

In the normal conditions shown in FIG. 20B, the mass member 410 and the link member 407 are positioned such that the center of mass of the link member and its attached mass member 410 assembly is positioned above a line passing though the center of the shaft 403 and parallel to the direction of the inertial igniter activation acceleration indicated by the arrow 414.

Now when the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is accelerated in the direction of the arrow 414, FIG. 20B, then the applied acceleration acting at the center of mass of the mass member 410 and the link member 407 assembly generates an inertial force in the opposite direction of the arrow 414, generating a clockwise torque that would tend to rotate the link member assembly in the clockwise direction. Then if the inertially generated torque is large enough to overcome the preloading torque of the torsion spring 415, FIG. 20A, then the link member assembly would begin to rotate in the clockwise direction. Now as the link member 407 rotates in the clockwise direction, the stop member 413 of the link member, FIG. 20B, engages the pin 411 of the shaft 403 and forces the shaft 403 to rotate in the clockwise direction with the clockwise rotating link member 407. If the activation acceleration in the direction of the arrow 414 persists, then at link member 407 continues to rotate in the clockwise direction, its generated clockwise torque balances with the preloaded torsion spring 415 torque, such as in the position shown by the dashed lines in FIG. 20B and indicated by the numeral 418.

Now as the link member 407 rotates in the clockwise direction as viewed in the schematic of FIG. 20B, then as the link member approaches close to its end positioning 418, its extended member 420 engages the extended member 419 of the second link member 408 and begins to rotate the link member 408 in the clockwise direction toward it positioning shown in the cross-sectional view D-D of FIG. 20A, shown in FIG. 20C, where the center of mass of the link member 408 and mass member 422 assembly is positioned above a line passing though the center of the shaft 403 and parallel to the direction of the inertial igniter activation acceleration indicated by the arrow 414.

The cross-sectional view D-D of FIG. 20A shown in FIG. 20C, the side view of the second inertially actuating link member 408 of the inertial spring winding component of the inertial igniter embodiment of FIG. 19 is shown. Similar to the link member 407, the link member 408 is also attached to the shaft 403 by the bearing 428 and is free to rotate over the shaft 403 within the range described below. As can be seen in FIG. 20C, the shaft 403 is also provided with a similar pin 423, which is positioned in the groove 424, which is similarly provided in the body of the link member 408 to accommodate it. In the position shown in FIG. 20C, the pin 423 has been rotated by the rotation of the link member 407 to the position shown close to the stop member 425, which is similarly provided inside the groove 424 of the link member 408. A mass member 422, similar to the mass member 410 of the link member 407, is also attached to the free side of the link member 408 as shown in FIG. 20C.

Now once the link member 408 has been rotated as was described above in the clockwise direction to the position shown in FIG. 20C, if the applied acceleration in the direction of the arrow 414 persists, then the applied acceleration would similarly act at the center of mass of the mass member 422 and the link member 408 assembly and generates an inertial force in the opposite direction of the arrow 414, thereby generating a clockwise torque that would tend to rotate the link member 408 assembly in the clockwise direction. Then if the inertially generated torque is large enough to overcome the preloading torque of the torsion spring 429, FIG. 20A, then the link member 408 assembly would continue to rotate in the clockwise direction. Now as the link member 408 rotates in the clockwise direction, the stop member 425 of the link member 408, FIG. 20C, would similarly engage the pin 423 of the shaft 403 and force the shaft 403 to further rotate in the clockwise direction with the clockwise rotation of link member 408. If the activation acceleration in the direction of the arrow 414 persists, then as the link member 408 continues to rotate in the clockwise direction, its generated clockwise torque balances with the preloaded torsion spring 429 torque, and similar to the link member 407, it would come to rest at some position similar to the position 418 of the link member 407.

Then similar to the link member 407, the link member 408 would engage the extended member 427 as it approaches close to its full clockwise rotation position, thereby moving the center of mass of the link member 409 and its attached mass member 430, FIG. 20A, to its “actuation” positioning, similar to the positioning of link member 408 seen in FIG. 20C, i.e., where its center of mass is above the line passing through the center of the shaft 403 as viewed in FIG. 20C and parallel to the direction of the activation acceleration indicated by the arrow 414, thereby allowing the link member 409 to begin to further rotate the shaft 403 as it was described for the link member 408.

It is, however, appreciated by those skilled in the art that by using the described method of sequentially rotating actuating link members with the provided mass members, the rotated shaft can only be rotated slightly less than 360 degrees (accounting for the size of the engaging shaft pins and stops in the link member grooves). In most inertial igniter applications, such amounts of shaft rotations are enough for proper winding of their torsion springs used to construct a “pendulum” based delay mechanism as it is described later. However, the “spring winding component” 401, FIGS. 20A, 20B and 20C, may be modified as described below to allow for effectively unlimited shaft rotation by the provision of the required number of link members and their required mass members.

The top view of an alternative inertially actuated “spring winding component” 401 of the inertial igniter embodiment 400 of FIG. 19 is shown in the schematic of FIG. 21A and is indicated by the numeral 431. The inertially actuated “spring winding component” 431 comprises at least one inertially actuation unit 432. In the schematic of FIG. 21A four such inertially actuation units 432, 433, 434, and 435 are shown. Except for the first inertially actuation unit 432, all other inertially actuation units, i.e., the units 433, 434, and 435 are in general identical.

As can be seen in the schematic of FIG. 21A, each of the inertially actuation units 432, 433, 434, and 435 comprises separate shafts (436 for the unit 432), which is free to rotate in a bearing (437 for the shaft 436), provided in the structure 406 of the inertial igniter embodiment. The shaft 436 is fixedly attached to the “gear section” 439 (shown in detail in FIG. 21), The “gear section” 439 is provided with a preloaded torsion spring 440, which is attached to the “gear section” 439 on one end and to the structure 406 of the inertial igniter on the other end. The preloaded torsion spring 440 biases the “gear section” 439 against the stop 456, FIG. 21B, which is provided on the structure 406 of the inertial igniter. An actuation mass member 441 is fixedly attached to the “gear section” 439 as can be seen in FIGS. 21A and 21B. The “gear section” 439 is in engagement with the gear 442, which is attached to the shaft 443 by a one-way clutch 445, FIG. 21B, as described below. The shaft 443 is attached to the structure 406 of the inertial igniter by bearings 444, which allow for its free rotation in the bearings.

It is appreciated that in the view of the schematic of FIG. 21A, the activation acceleration is still considered to be perpendicular to the plane of the view and pointing out of the plane.

FIG. 21B shows the view E-E of the alternative inertially actuated “spring winding component” 431 of FIG. 21A of the inertial igniter embodiment 400 of FIG. 19. In normal conditions, the preloaded torsion spring 440 (not shown in FIG. 21), FIG. 20A, applies a counterclockwise torque to the “gear section” 439 as viewed in FIG. 21B, which biases the “gear section” 439 against the stop 456, which is provided on the structure 406 of the inertial igniter embodiment 400. It is noted that the stop 456 is not shown in the schematics of FIGS. 19 and 21A for the sake of clarity. Similar stop members are also provided for all “gear sections” of the inertially actuation units 432, 433, 434, and 435, FIG. 21A, and are also not shown for the sake of view clarity.

In the normal conditions shown in FIG. 21B, the mass member 441 and the “gear section” 439 are positioned such that the center of mass of their assembly is positioned above a line passing though the center of the shaft 436 and parallel to the direction of the inertial igniter activation acceleration indicated by the arrow 447.

Now when the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is accelerated in the direction of the arrow 447, FIG. 21B, then the applied acceleration acting at the center of mass of the mass member 441 and the “gear section” 439 assembly generates an inertial force in the opposite direction of the acceleration arrow 447, generating a clockwise torque that would tend to rotate the mass member 441 and the “gear section” 439 assembly in the clockwise direction as viewed in FIG. 21B. Then if the inertially generated torque is large enough to overcome the preloading torque of the torsion spring 440, FIG. 21A, then the assembly would begin to rotate in the clockwise direction.

Now as the mass member 441 and the “gear section” 439 assembly rotates in the clockwise direction, the teeth of the gear section 446, which are in engagement with mating teeth of the gear 442 would rotate the gear 442 in the counterclockwise direction. Here, the one-way clutch 445 connecting the gear 442 to the shaft 443 is selected to be the type that engages the gear 442 to the shaft 443 as the gear is rotated in the counterclockwise direction but would allow free rotation of the gear 442 over the shaft 443 when the gear 442 is rotated in the clockwise direction as viewed in FIG. 21B, ending up in the position shown by dashed lines in FIG. 21C. As a result, as the mass member 441 and the “gear section” 439 assembly is rotated in the clockwise direction due to the activation acceleration in the direction of the arrow 447, the shaft 443 is rotated in the counterclockwise direction by the gear 442.

FIG. 21D shows the view F-F of the alternative inertially actuated “spring winding component” 431 of FIG. 21A of the inertial igniter embodiment 400 of FIG. 19. In normal conditions, the preloaded torsion spring (440 for inertially actuating unit 432—not shown in FIG. 21D for unit 433), FIG. 20A, applies a counterclockwise torque to the “gear section” 451 (shown in solid black lines) as viewed in FIG. 21D, which biases the “gear section” 451 against the stop 450 (shown in dashed lines), which is provided on the structure 406 of the inertial igniter embodiment 400. The “gear section” 451 is in engagement with the gear 452, which is also attached to the shaft 443 by a one-way clutch 457.

Now as the mass member 441 and the “gear section” 439 assembly of the first inertially actuating unit 432 (shown in solid light lines and indicated by the numeral 449) rotates in the clockwise direction as viewed in the schematic of FIG. 21D, then as the assembly approaches close to its end positioning 449, its extended member 448 engages the extended member 454 of the “gear section” 451 of the second link inertially actuating unit 433, and begins to rotate the “gear section” 451 and its attached mass member 453 in the clockwise direction toward it positioning shown in the view F-F of FIG. 21D in solid black lines, where the center of mass of the mass member 453 and the “gear section” 451 assembly is positioned above a line passing though the center of the shaft 455 and parallel to the direction of the inertial igniter activation acceleration indicated by the arrow 447.

Now once the “gear section” 451 and mass member 453 assembly has been rotated in the clockwise direction as was described above to the position shown in FIG. 20D (solid black lines), if the applied acceleration in the direction of the arrow 447 persists, then the applied acceleration would similarly act at the center of mass of the “gear section” 451 and mass member 453 assembly and generates an inertial force in the opposite direction of the arrow 447, thereby generating a clockwise torque that would tend to rotate the “gear section” 451 and mass member 453 assembly in the clockwise direction. Then if the inertially generated torque is large enough to overcome the preloading torque of the torsion spring 458, FIG. 21A, then the “gear section” 451 and mass member 453 assembly would continue to rotate in the clockwise direction.

Now as the “gear section” 451 and mass member 453 assembly rotates in the clockwise direction, the teeth of the gear section 459 of the “gear section” 451, which are in engagement with the gear 452 would rotate the gear 422 in the counterclockwise direction. Here, the one-way clutch 445 connecting the gear 452 to the shaft 443 is also selected to be the type that engages the gear 452 to the shaft 443 as the gear 452 is rotated in the counterclockwise direction but would allow free rotation of the gear 452 over the shaft 443 when the gear 452 is rotated in the clockwise direction as viewed in FIG. 21D. As a result, “gear section” 451 and mass member 453 assembly is rotated in the clockwise direction due to the activation acceleration in the direction of the arrow 447, the shaft 443 is further rotated in the counterclockwise direction by the gear 452.

Then similar to the “gear section” 439 and mass member 441 assembly, the extended member 460 of the “gear section” 451 would engage the extended member of the “gear section” and mass member assembly of the inertially actuating unit 434, rotate it in the clockwise direction as was done for the “gear section” 451 and mass member 453 assembly, and position it to further rotate the shaft 443 as was described for the “gear section” 451 and mass member 453 assembly. It is appreciated that as long as the activation acceleration in the direction of the arrow 447 persists, the inertially actuating unit 434 would then similarly rotate the “gear section” and mass member assembly of the inertially actuating unit 435 in the clockwise direction to its actuation configuration as shown for the “gear section” 451 and mass member 453 assembly, FIG. 21D, and allow it to further rotate the shaft 443 in the counterclockwise direction as was described above for the inertially actuating unit 434.

It is appreciated that in general, the inertially actuating units of the “spring winding components” 401 and 431 of FIGS. 20A and 21A, respectively, of the inertial igniter embodiment 400 of FIG. 19 are configured to be identical if the torsion spring being wound has a nearly constant torque spring in the winding range. However, if the resistance of the torsion spring to winding increases with increased winding rotation, then the actuating torque of the inertially actuating units must increase from one unit to the next. In the present method of designing the described inertially actuating units, this is readily accomplished by either increasing the mass member of a unit, such as the mass member 422 of the second unit of the “spring winding components” 401, FIG. 20A, or by increasing the radial distance of the mass member from the unit shaft, or by their combination.

It is appreciated by those skilled in the art that similar to the “spring winding component” 431 of FIG. 21A, the inertially actuating link member 407, 408 and 409 and other ones that may be provided for the “spring winding component” 401 of FIG. 20A may also have separate shafts, which are connected to each other by one-way clutches or ratchets or the like to transfer each inertially actuating link member rotation to the output shaft 463. The connection between the shafts of two consecutive inertially actuating link member, in this case the members 407 and 408, are shown in the schematic of FIG. 20D.

As can be seen in the schematic of FIG. 20D, in this modified “spring winding component” 401 of FIG. 20A, the inertially actuating link members 407 and 408 are shown to be provided with separate shafts 516 and 517, respectively. The first inertially actuating link members 407 is fixedly attached to its shaft 516, while the remaining inertially actuating link members, in this case member 408, are attached to their shaft (517 for the member 408), by one-way clutches as was described for the “spring winding component” 401 of FIG. 20A. The shafts 516 and 517 are free to rotate in the bearings 518 and 519, provided in the structure 406 of the inertial igniter embodiment 400 of FIG. 19. The shafts 516 and 517 are then connected by one-way clutch 515 (or a ratchet or the like functioning coupling element), which allows for clockwise rotation of the shaft 516 due to clockwise rotation of the inertially actuating link member 407, as viewed in the cross-sectional view C-C in FIG. 20B, to rotate the shaft 517 in the clockwise direction. The sequential actuation of the remaining inertially actuating link members would continue rotating the shaft of the next inertially actuating link member as was described for the “spring winding component” 401 of FIG. 20A.

The top view of the mechanical delay component 461 of the lateral and spin acceleration and spin velocity insensitive long duration mechanical inertial igniter embodiment 400 of FIG. 19 is shown in FIG. 22. In the schematic of FIG. 22, the input shaft 462, which is the output of the “spring winding component” 401 of the inertial igniter embodiment 400 of FIG. 19 is considered to drive the mechanical delay mechanism as described below. The input shaft 462 may be the output shaft 463 or 464 of the “spring winding component” of FIGS. 20A and 21A, respectively.

As can be seen in the top view of FIG. 22 of the mechanical delay component 461 of the inertial igniter embodiment 400 of FIG. 19, the mechanical delay mechanism is driven by the input shaft 462 of the “spring winding component” of the inertial igniter, which is free to rotate in the bearing 472 that is provided in the structure 406 of the inertial igniter. The input shaft 462 is used to drive the “spring winding rotation” mechanism 465, the design and operation of which is described later through the view G-G, which is used to rotate the gear 466 of the mechanical delay component 461. The gear 466 is fixedly attached to the shaft 475, which is free to rotate in the bearing 476, provided in the structure 406 of the inertial igniter. The gear 466 is in engagement with the pinion 467, which is fixedly attached to the shaft 468, which is free to rotate in the bearing 473, which is also provided in the structure 406 of the inertial igniter embodiment 400 of FIG. 19. An inertia wheel 469 is also fixedly mounted on the shaft 468. The inertia wheel 469 is intended to provide large enough moment of inertial about the axis of rotation of the shaft 468 to provide the required period of oscillation to achieve the prescribed mechanical delay time of the inertial igniter as described later. A torsion spring 470 is also provided about the shaft 468 as shown in the schematic of FIG. 22. The torsion spring 470 is attached to the inertia wheel 469 on one end and to the structure 406 of the inertial igniter on the other end 471. In normal conditions, the torsion spring 470 is in its free state.

The cross-sectional view G-G of FIG. 22, showing the components of the “spring winding rotation” mechanism 465 and its engaging gear member of the mechanical delay mechanism component of the mechanical inertial igniter embodiment 400 of FIG. 19, is shown in FIG. 22A. As can be seen in the schematic of FIG. 22A, the “spring winding rotation” mechanism 465 consists of the link 477, which is fixedly attached to the input shaft 462 of the mechanical delay component 461 of the inertial igniter. It is appreciated that in the schematic of FIG. 22A, the cross-sectional view G-G of FIG. 22 is shown in its normal condition.

The link 477 is provided with a groove 478, within which the sliding member 479 is free to displace. A compressive spring 480 is also seen to be provided in the groove 478 behind the sliding member 479. In the normal conditions seen in the schematic of FIG. 22A, the compressive spring 480 is unloaded and in its free length, positioning the link as can be seen in FIG. 22A. The compressive spring 480 is fixedly attached to the bottom surface of the groove 478 on one end and to the bottom of the sliding member 479 on the other end as viewed in the schematic of FIG. 22A.

In normal conditions, the compressive spring 480 is seen in the schematic of FIG. 22A to position the link 479 such that the link member 481 is positioned to engage the pin 483 of the gear 466. The link member 481 is attached to the sliding member 479 by the rotary joint 482. A preloaded torsion spring (not shown) is also provided at the rotary joint 482 to bias the link member 481 against the stop 484, which is fixedly attached to the sliding member 479.

The mechanical delay component 461 of the inertial igniter embodiment 400 of FIG. 19 is also provided with a gear 466 release member 474, which is fixedly attached to the structure 406 of the inertial igniter as can be seen in FIGS. 22 and 22A. As can be seen in FIG. 22, a relatively small gap 485 is provided between the release member 474 and all the components of the “spring winding rotation” mechanism 465, FIG. 22A, except for the link member 481, which is “thick” enough (in the direction normal to the plane of view of FIG. 22A) to engage the surface 486 of the release member 474 as the link 477 rotates in the clockwise direction to wind the torsion spring 470, FIG. 22, as described below. The height of the pin 483 of the gear 466 is also short enough to clear the release member 474.

The “spring winding rotation” mechanism 465 and its engaging gear member of the mechanical delay mechanism component of the mechanical inertial igniter embodiment 400 of FIG. 19 functions as follows, FIGS. 22 and 22A. When the device to which the inertial igniter is attached is subjected to the prescribe acceleration (direction of the arrow 414 in FIG. 20B or 447 in FIG. 21C, depending on which of the disclosed “spring winding component” is employed in the inertial igniter), then the input shaft 462 (output shaft 463 or 462 of the “spring winding component” of FIGS. 20A and 21A, respectively) is rotated in the clockwise direction as viewed in the schematic of FIG. 22A as was described previously for the “spring winding component” of the inertial igniter embodiment 400 of FIG. 19.

Now, as the shaft 462 is rotated in the clockwise direction, FIG. 22A, the link 477, which is fixedly attached to the shaft 462 would also rotate with it in the clockwise direction. The clockwise rotation of the link 477 would then rotate with it the sliding member 479, which would in turn engage the link member 481 with the pin 483 of the gear 466 and begin to rotate the gear 466 in the clockwise direction. It is appreciated that the stop 484 of the sliding member 479 prevents counterclockwise rotation of the link member 481 relative to the sliding member 479 as shown in FIG. 22B.

It is appreciated that if while the shaft 462 is being rotated in the clockwise direction and rotating with it the gear 466 the applied activation acceleration ceases or drops below its prescribed level, then the preloaded torsion springs (for example, 415 for the inertially actuating link member 407, FIG. 20A and other inertially actuating link members, FIGS. 20A and 21A) would return the inertially actuating link members to their initial and pre-activation acceleration application, therefore the input shaft 462 would rotate back in the counterclockwise direction to its initial positioning of FIG. 22A together with the “spring winding rotation” mechanism 465 and the gear 466.

However, if the applied activation acceleration continues, the link 477 continues to be rotated in the clockwise direction until the tip 487 of the link member 481 comes into contact with the surface 486 of the release member 474 as shown in FIG. 22C. Then as the link 477 is rotate further, the inclined surface 486 would begin to push the link member 481 and thereby the sliding member 479 back into the grove 478 in the link 477. Thereby as the link 477 further rotates in the clockwise direction, then at some point, the tip 487 of the link member 481 disengages the pin 483 of the gear 466 as shown in FIG. 22D. In FIG. 22D, this positioning of the “spring winding rotation” mechanism 465 is indicated by the numeral 488, noting that in this instant of pin 483 disengagement by the link member 481, the pin 483 in under the release member 474.

Then once the link member 481 has disengaged the pin 483 of the gear 466, the gear 466 is free to begin to rotate back in the counterclockwise direction as described later. The link 477 would then rotate certain amount further in the clockwise direction to ensure pin 483 release and may even be rotated past the surface 486 of the release member 474 as shown in dashed lines in FIG. 22D and indicated by the numeral 489. It is appreciated that when the applied activation acceleration ceases, the inertially actuating links of the “spring winding component” (401 of FIG. 20A or 431 of FIG. 21A) are rotated back to their initial positioning by their preloaded torsion springs as was previously described. Thereby the “spring winding rotation” mechanism 465 would return to its initial positioning of FIG. 22A.

It is appreciated by those skilled in the art that the above-described process of “spring winding rotation” mechanism 465 returning to its initial positioning when the applied acceleration in the direction of the activation acceleration has ceased is configured to satisfy the need for the inertial igniter embodiment 400 of FIG. 19 to be resettable. The other components of the inertial igniter embodiment 400 of FIG. 19 is also shown later to satisfy the ability to reset if the applied acceleration in the direction of the activation acceleration does not satisfy the prescribed acceleration level and duration requirement.

It is appreciated that in the designs in which the “spring winding rotation” mechanism 465 is rotated past the release member edge 490 as shown by dashed lines in FIG. 22D, then while the link 477 is being rotated back in the counterclockwise direction, the link member is rotated in the counterclockwise direction relative to the sliding member 479 by the edge 490 of the release member 474 until it can clear the top surface 486 of the release member, thereby allowing the “spring winding rotation” mechanism 465 to return to its initial positioning of FIG. 22A. It is also appreciated that if the “spring winding rotation” mechanism 465 and the release member 474 are configured to stop clockwise rotation of the link 477 once the pin 483 of the gear 466 has been released, for example, by providing a stop member 491, FIG. 22D, then the sliding member 479 and the link member 481 may be integrated as one element.

It is appreciated that while the gear 466 is being rotated in the clockwise direction as was described above and shown in the schematics of FIGS. 22A, 22B, 22C and 22D, the gear 466 would rotate the pinion 467 in the counterclockwise direction as shown in the view of FIG. 22A by dashed line and indicated by the numeral 492, which would in turn rotate the shaft 468 and thereby the inertia wheel 469 in the same direction, FIG. 22. The inertia wheel 469 would then wind the torsion spring 470 from its unloaded state.

Now once the link member 481 of the “spring winding rotation” mechanism 465 disengages the pin 483 of the gear 466, FIG. 22D, then the potential energy stored in the torsion spring 470 would begin to rotationally accelerate the inertial wheel 469 together with its fixedly attached shaft 468 and the pinion 467 and its engaged gear 466.

It is appreciated by those skilled in the art that the inertia wheel 469, together with the shaft 468, the pinion 467 and the gear 466 would then form the moment of inertia of a rotationally oscillating mechanical system together with the torsion spring 470. In this oscillating mechanical system, assuming no frictional losses, the potential energy stored in the torsion spring 470 is transferred to rotational kinetic energy of the inertia wheel 469, the shaft 468, pinion 467 and its engaging gear 466 until they gain their maximum speed, i.e., until all the torsion spring potential energy is transferred to their kinetic energy, followed by the return of the kinetic energy back to the torsion spring as potential energy, with the entire cycle constituting one period of oscillation of the oscillatory motion of the described mechanical system.

It is also appreciated by those skilled in the art that the total moment of inertia of the above mechanical oscillating system I_tot is therefore given asI_tot=I_w+I_ws+I_p+I_G/N²  (5)where, I_w is the moment of inertia of the inertia wheel 469, I_ws is the moment of inertial of the shaft 468, I_p is the moment of inertial of the pinion 467, I_G is the combined moment of inertia of the gear 466 and the shaft 475, and Nis the gear ratio of the gear 466 and the pinion 467.

It is appreciated by those skilled in the art that for with the above total moment of inertial I_tot of the above oscillating mechanical system, with a constant spring rate K_TS of the torsion spring 470, the oscillating (vibrating) mechanical system of FIG. 22 would be oscillating (vibrating) at a natural frequency of

$\begin{array}{cc}\omega =\sqrt{\frac{K_{\mathrm{TS}}}{I_{\mathrm{tot}}}}& \left(6\right)\end{array}$ where ω (radian second) is the natural frequency of vibration of the torsional vibration system of FIG. 22. The period T of each cycle of vibration (oscillation) of the torsional vibration system is then given as

$\begin{array}{cc}T=\frac{2\pi }{\omega }\mathrm{seconds}& \left(7\right)\end{array}$

It is appreciated that as can be seen in equation (5), the total moment of inertia I_tot of the oscillating system of FIG. 22 is mainly due to the larger inertia wheel 469, i.e., I_w. The gear ratio N, which is larger than unity would also reduce the contribution of the inertia of the gear 466 to the total moment of inertia.

It is also appreciated that when longer oscillation period T, equation (7), is desired, the natural frequency ω, equation (6), of the oscillating (vibrating) system must be reduced. As can be seen from the equation (6), this can be achieved by either reducing the spring constant K_TS, i.e., by selecting a softer torsion spring, or by increasing the total moment of inertial I_tot of the system, or both. However, to increase the total moment of inertia of the system, the size of its components, mainly the inertia wheel, must be increased. This is usually not desirable since it would make the inertia igniter embodiment 400 of FIG. 19 larger and heavier. However, the goal of significantly reducing the natural frequency of the mechanical delay component 461 of FIG. 22 may be achieved by modifying its design through rearrangement of several of its components as described below.

FIG. 23 illustrates the top view of a modified mechanical delay component 493 of the embodiment of FIG. 22 for the lateral and spin acceleration and spin velocity insensitive long duration mechanical inertial igniter embodiment of FIG. 19. As can be seen in the schematic of FIG. 23, all components of the modified mechanical delay component 493 are identical to those of the mechanical delay component 461 of FIG. 22 and are indicated by the same numerals, except for the following.

As can be seen in the schematic of FIG. 23, the first modification consists of attaching the winding torsion spring 494 (470 in FIG. 22) to the shaft 495 (475 in FIG. 22) of the gear 466 instead of the shaft 468 and the inertia wheel 498 (469 in FIG. 22). In this modified mechanical delay component 493, the torsion spring 494 is attached on one end to the shaft 495 of the gear 466 and to the structure 406 of the inertial igniter on the other end. As a result, the torsion spring 494 is wound directly by the rotation of the gear 466. The shaft 495 is still free to rotate in the bearings 496 that are provided in the structure 406 of the inertial igniter embodiment 400 of FIG. 19. The inertia wheel 498 (469 in FIG. 22) is still fixedly attached to the shaft 468, together with the pinion 467.

It is appreciated that the cross-sectional view G-G of the modified mechanical delay component 493 of FIG. 23 is identical to those of the mechanical delay component 461 of FIG. 22 as shown in the schematic of FIG. 22A during its initial state prior to the application of the activation acceleration, and as an activation acceleration is applied to the inertial igniter and the gear 466 is rotated in the clockwise direction as shown in the schematics of FIGS. 22B, 22C and 22D, when the gear 466 is released as was described previously.

Then once the link member 481 has disengaged the pin 483 of the gear 466 as is shown in the schematic of FIG. 22D, the gear 466 is free to begin to rotate back in the counterclockwise direction. It is appreciated that when the applied activation acceleration ceases, the inertially actuating links of the “spring winding component” (401 of FIG. 20A or 431 of FIG. 21A) are rotated back to their initial positioning by their preloaded torsion springs as was previously described. Thereby the “spring winding rotation” mechanism 465 would also return to its initial positioning of FIG. 22A.

It is appreciated that while the gear 466 is being rotated in the clockwise direction as was described above and shown in the schematics of FIGS. 22A, 22B, 22C and 22D, the shaft 495 of the gear 466 would wind the torsion spring 470 from its unloaded state. In the meantime, the gear 466 would rotate the pinion 467 and thereby the inertia wheel 498 as can be seen in the schematic of FIG. 23 of the modified mechanical delay component 493.

Now once the link member 481 of the “spring winding rotation” mechanism 465 disengages the pin 483 of the gear 466, FIG. 22D, then the potential energy stored in the torsion spring 494 would begin to rotationally accelerate the gear 466 and its fixedly attached shaft 495, while the gear 466 would rotationally accelerate the pinion 467 and its fixedly attached shaft 468 and thereby the inertia wheel 498.

It is appreciated by those skilled in the art that the inertia wheel 498, together with the shaft 468, the pinion 467 and the gear 466 and its shaft 495 would then form the moment of inertia of a rotationally oscillating mechanical system together with the torsion spring 494. In this oscillating mechanical system, assuming no frictional losses, the potential energy stored in the torsion spring 494 is transferred to rotational kinetic energy of the inertia wheel 498, shaft 468, pinion 467 and its engaging gear 466 and its shaft 495 until they gain their maximum speed, i.e., until all the torsion spring potential energy is transferred to their kinetic energy, followed by the return of the kinetic energy back to the torsion spring as potential energy, with the entire cycle constituting one period of oscillation of the oscillatory motion of the described mechanical system.

It is also appreciated by those skilled in the art that the total moment of inertia of the above mechanical oscillating system I_T is therefore given asI_T=N²(I_w+I_ws+I_p)+I_G+I_GS  (8)where, I_w is the moment of inertia of the inertia wheel 498, I_ws is the moment of inertial of the shaft 468, I_p is the moment of inertial of the pinion 467, I_G is the combined moment of inertia of the gear 466 and I_GS is the moment of inertia the shaft 495, and Nis the gear ratio of the gear 466 and the pinion 467.

It is appreciated by those skilled in the art that for with the above total moment of inertial I_T of the above oscillating mechanical system, with a constant spring rate K_TS of the torsion spring 494, the oscillating (vibrating) mechanical system of FIG. 23 would be oscillating (vibrating) at a natural frequency of

$\begin{array}{cc}\omega =\sqrt{\frac{K_{\mathrm{TS}}}{I_T}}& \left(9\right)\end{array}$ where ω (radian second) is the natural frequency of vibration of the torsional vibration system of FIG. 23. The period T of each cycle of vibration (oscillation) of the torsional vibration system is then given as

$\begin{array}{cc}T=\frac{2\pi }{\omega }\mathrm{seconds}& \left(10\right)\end{array}$

It is appreciated that as can be seen in equation (8), the total moment of inertia I_T of the rotationally oscillating (vibrating) system of FIG. 23 is significantly larger than the total moment of inertia I_tot of the rotationally oscillating (vibrating) system of FIG. 22. This is obviously the case due to the change in the positioning of the torsion spring 494, in which the inertia wheel 498 is rotated by the gear ration factor N more than the rotational winding and unwinding of the torsion spring 494.

As a result, as it was previously described, by significantly increasing the total moment of inertia of the rotationally oscillating (vibrating) system of FIG. 23 while keeping its torsion spring rate the same, the natural frequency ω, equation (9), of the rotationally oscillating (vibrating) system of FIG. 23 becomes significantly smaller than the natural frequency ω, equation (6), of the rotationally oscillating (vibrating) system of FIG. 22. The period of oscillation T of the rotationally oscillating (vibrating) system of FIG. 23 is similarly significantly longer than that of the rotationally oscillating (vibrating) system of FIG. 22.

It is therefore appreciated that the mechanical delay component 493 of FIG. 23 is more suitable for inertial igniter embodiment 400 of FIG. 19 that must provide longer time delay, i.e., for inertial igniters with prescribe initiation activation requirements of activation accelerations with relatively long duration, for example, durations that may be 100 msec or more. The mechanical delay component 493 of FIG. 23 is clearly superior for long duration activation acceleration applications since for the same period of oscillation, their designs are smaller and lighter than their mechanical delay component alternative of FIG. 22, which is highly desirable for munitions and most other applications.

It is also appreciated that in addition to increasing the total moment of inertia of the rotationally oscillating (vibrating) system of FIG. 23 by increasing the size of its inertia wheel 498 or by making its torsion spring 494 softer, i.e., reducing its spring rate K_TS, one may also use additional gearing to achieve the same goals. Examples of additional gearing to reduce the equivalent spring constant of the rotational oscillating (vibrating) system and its equivalent moment of inertia with the goal of reducing the system natural frequency and thereby increasing it period of oscillation are provided below.

FIG. 24 shows the modified mechanical delay component 493, indicated by the numeral 500, in which by the addition of a pair of gears, the equivalent spring rate of the torsion spring of the rotationally oscillating (vibrating) system of the mechanical delay component is significantly reduced. In this modified mechanical delay component, a pinion 501 is also fixedly attached to the shaft 502 (495 in FIG. 23), to rotate together with the gear 466. A gear 503 is then meshed with the pinion 501, which is fixedly attached to the shaft 504, which is free to rotate in the bearing 507, provided in the structure 406 of the inertial igniter embodiment 400 of FIG. 19. The torsion spring 505 of the rotationally oscillating (vibrating) system of the mechanical delay component 500 is then mounted on the shaft 504 of the gear 503, where it is attached to the shaft 504 on one end and to the structure 406 of the inertial igniter on the other end.

It is appreciated by those skilled in the art that by providing the gear 503 and pinion 501 to reduce the ratio between the winding rotation of the torsion spring 505 and the rotation of the gear 466, the equivalent spring rate K_TS, equation (9), of the rotationally oscillating (vibrating) system of the mechanical delay component 500 of FIG. 24 is proportionally reduced. As a result, the natural frequency ω, equation (9), of the oscillating mechanical system is also reduced and its period of oscillation, equation (10), is increased.

FIG. 25 shows the modified mechanical delay component 493, indicated by the numeral 510, in which by the addition of a pair of gears, the total moment of inertia of the rotationally oscillating (vibrating) system of the mechanical delay component is significantly increased. In this modified mechanical delay component, a gear 509 is fixedly attached to the shaft 468 of the pinion 467 as shown in FIG. 25. The gear 509 would then engage the pinion 511, which is fixedly attached to the shaft 512. The shaft 512 is free to rotate in the bearing 513, which is provided in the structure 406 of the inertial igniter embodiment 400 of FIG. 19. The system inertia wheel 514 is then fixedly attached to the shaft 512.

It is appreciated by those skilled in the art that by providing the gear 509 and pinion 511, the gear ratio between the gear 466 and pinion 511 is now increased by the ratio between the gear 509 and pinion 511. The effective total moment inertial I_T, equation (8), is thereby increased toI_T=N²N₁²(I_w+I_ws+I_P1)+N²(I_p+I_G+I_GS)+I_G+I_GS(I_w+I_ws=I_p)+I_G+I_GS  (8)where, I_w, I_ws and I_P1 are the moments of inertial of the inertial wheel 514, its shaft 512, and the pinion 511, respectively; I_p, I_G1, and I_GS are the moments of inertia of the gear 509, pinion 467 and their shaft 468, respectively; I_G, and I_GS are the moments of inertia of the gear 466 and its shaft 495, respectively; and N and N₁ are the gear ratios between the gears 466 and pinion 467 and gear 509 and pinion 511, respectively. As a result, by significantly increasing the total moment of inertia I_T, equation (9), the natural frequency ω of the oscillating mechanical system is significantly reduced and its period of oscillation, equation (10), is similarly increased.

FIG. 26 shows the side view “H” of the inertial igniter striker mechanism component 402 of the inertial igniter embodiment 400 of FIG. 19, together with the striker releasing rotationally oscillating gear member 466. The initiator striker mechanism component 402 consists of the striker member 520, which is attached to the structure 406 of the inertial igniter embodiment 400 of FIG. 19 by the rotary joint 521, via a support member 522. The striker member 520 is also provided with a preloaded torsion spring 526, which in the pre-activation state of the inertial igniter embodiment 400, biases the tip 527 of the striker member against the tip 528 of the striker release member 523. The preloaded torsion spring 526 is fixedly attached to the structure 406 of the inertial igniter on one end and to the striker member 520 at its other end 529. As can be seen in the schematic of FIG. 26, the striker release member 523 is attached to the structure 406 of the inertial igniter by the rotary joint 524 via the support member 525. A lightly preloaded compressive spring 560 is also provided to bias the striker release member against the striker member tip 527 as shown in FIG. 26. The compressive spring 560 is attached to the structure 406 of the inertial igniter on one end and to the striker release member on the other end as can be seen in FIG. 26. The striker member 520 is provided with the sharp tip member 568, which is configured to initiate the percussion primer 569 upon impact as described later, the ignition flame and sparks would then to exit through the provided opening 570 of the inertial igniter embodiment 400 of FIG. 19.

As can be seen in the schematic of FIG. 26, a member 562 is fixedly attached to the side surface of the gear 466 (behind the gear as viewed in FIG. 26 and clearing the gear teeth), to which a link member 563 is attached by the rotary joint 564. The link member 563 is biased against the stop 565, which is fixedly attached to the member 562, by a preloaded torsion spring (not shown) provided at the joint 564. In the configuration shown in the schematic of FIG. 26, the gear 466 is rotating in the counterclockwise direction as shown by the arrow 561 and the tip 566 of the link member 563 is about to strike the tip 567 of the striker release member 523. The operation of the initiator striker mechanism component 402 and the inertial igniter embodiment 400 of FIG. 19 are described below.

The inertial igniter embodiment 400 of FIG. 19 operates as follows. It is noted that the following description of the operation of this inertial igniter embodiment is the same for all described variations of its components, whether “spring winding component” 401 or 431 of FIGS. 20A and 21A, respectively, is used in its construction; or if mechanical delay component 461 or 493 or 500 or 510 of FIGS. 22, 23, 24 and 25, respectively, is used in its construction. The only difference between the different combinations of the above components in the construction of the inertial igniter 400 of FIG. 19 is mostly in the compactness of the device and the length of delay time that can be achieved as described for each of the above components of the inertial igniter.

The operation of the inertial igniter embodiment 400 of FIG. 19 is described here using the side view “H” of the initiator striker mechanism component 402 of the inertial igniter together with the striker releasing rotationally oscillating gear member 466 of FIG. 26. Several operational scenarios are however possible, depending on the required duration of the prescribed activation acceleration as described below.

Considering that in the schematic of FIG. 26, the gear member 466 is in its rest position, i.e., before the inertial igniter embodiment 400 of FIG. 19 is subjected to any acceleration in the activation direction. It is appreciated that in this configuration of the inertial igniter mechanisms, the torsion spring 470 of FIG. 22, 494 of FIGS. 23 and 25, and 505 of FIG. 24 are in their free (unloaded) state. Now when the device to which the inertial igniter is attached is subjected to the activation acceleration, then the inertially actuating link members of the “spring winding component” 401 or 432 of FIGS. 20A and 21A, respectively, that is being used would begin to rotate the gear member 466, FIG. 26, in the clockwise direction as viewed in the schematic of FIG. 26.

In FIG. 27, the gear member 466 and the striker release member 523 are redrawn. In this illustration, the arrow 571 shows the direction of inertially actuating link members of the “spring winding component” rotating the gear member 466 and winding the torsion spring of the mechanical delay component 461 of the inertial igniter, FIG. 19, and the arrow 572 shows the (counterclockwise) direction of the gear member 466 rotation once it is released by the “spring winding rotation” mechanism 465.

Now, consider the scenario when the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is subjected to the activation acceleration, and that the inertially actuating link members of the “spring winding component” used in the inertial igniter, i.e., “spring winding component” 401 or 432 of FIGS. 20A and 21A, respectively, would rotate the gear member 466, FIG. 26, in the clockwise direction from its position shown in FIG. 26 to the position shown in FIG. 27 and indicated by the arrow 571, at which point the gear is released by the “spring winding rotation” mechanism 465 as was previously described, FIG. 22D. As can be seen in the schematics of FIGS. 26 and 27, the gear 466 is shown to have been rotated in the clockwise direction around 270 degrees. As a result, the torsion spring of the mechanical delay component 461, i.e., the torsion spring 470 of FIG. 22, 494 of FIGS. 23 and 25, and 505 of FIG. 24, is also wound the same amount.

In the following description of the operation of the inertial igniter embodiment 400 of FIG. 19, the mechanical delay component of FIG. 22 is used to describe the operation of the inertial igniter up to the point of its percussion primer initiation. It is appreciated that the same process also applies when other above mechanical delay components are used in the construction of the inertial igniter.

Now, when the gear member 466 is released from its positioning of FIG. 27, the gear member is rotationally accelerated by the torque of the wound torsion spring 470, FIG. 22, in the counterclockwise direction as viewed in the schematics of FIGS. 26 and 27, and as shown by the direction of the arrow 572, until the tip 566 of the link member 563 strikes the tip 567 of the striker release member 523, causing it to rotate in the clockwise direction as viewed in the schematic of FIG. 28, thereby causing the tip 528 of the striker release member 523 to disengage the tip 527 of the striker member 520. The striker member is then rotationally accelerated in the counterclockwise direction by the preloaded torsion spring 526. The moment of inertia of the striker member about the axis of rotation of the rotary joint 521 and the preloading level and spring rate of the torsion spring 526 are selected such that the striker member gains enough kinetic energy as its sharp tip 568 strikes the percussion primer 569, as shown in FIG. 28, to reliably initiate it. The ignition flame and sparks would then exit from the opening 570 in the structure of the inertial igniter.

It is appreciated by those skilled in the art that since the oscillatory mechanical delay mechanism 461 and its various modifications described previously is in its rest position before the start of its torsion spring 470 winding, i.e., zero potential energy configuration of the torsion spring, FIG. 22, and the gear 466 and its link member 563 assembly is positioned as shown in FIG. 26, i.e., close to the tip 567 of the striker release member 523, therefore the time that it takes for the gear 466 to rotate in the counterclockwise direction from its releasing position shown in FIG. 27 until the tip 566 of the link member 463 strikes the tip 567 of the striker release member 523 and rotate it in the clockwise direction to release the striker member 520 is a quarter of the period of oscillation of the oscillatory mechanical delay mechanism of FIG. 22, at which time. The natural frequency ω and the resulting period of oscillation T for the oscillatory mechanical delay mechanism of FIG. 22 are given by equations (6) and (7), respectively. As a result, the time that it takes for the counterclockwise rotation of the gear 466 from its release as shown in the configuration of FIG. 27 to impact and release the striker release member 523, FIG. 28, becomes t=T/4, where T is given by equation (7).

It is appreciated that at the time of tip 566 of the link member 463 striking the tip 567 of the striker release member 523, the gear 466 is rotating in the counterclockwise direction at its peak of its oscillatory rotational velocity due to the transfer of the entire potential energy stored in the wound torsion spring 470 to the kinetic energy of the rotating components of the mechanical delay mechanism, which includes the gear 466. The mechanical delay mechanism, FIG. 22, if properly configured, should therefore have enough kinetic energy to rotate the striker release member 523 in the clockwise direction upon impact enough to release the striker member as was described above.

In the configuration of FIG. 26, in the resting positioning of the gear 466, the link member 563 assembly is positioned close to the tip 567 of the striker release member 523. This is the reason that once the gear 466 is rotated in the clockwise direction to wind the torsion spring 470, for example to the position shown in FIG. 27 as was previously described, then upon its release, the gear would take a quarter of the period of oscillation, i.e., t=T/4, to rotate back in the counterclockwise direction to its initial positioning of FIG. 26 and impact and rotate the striker release member 523 in the clockwise direction and release the striker member 520. With the above initial positioning of the gear 466, the gear 466 is at its peak counterclockwise rotational speed during the striker release member 523 impact, which considering the fact that the striker release member geometry and preloaded spring 560, FIG. 26, are configured to require a relatively small force to rotate in the clockwise direction enough to release the striker member 520, therefore the gear 466 does not have to be at its peak counterclockwise rotational velocity as it impacts the striker release member 523. This characteristic of the present oscillatory mechanical delay mechanism may be used as described below to increase the aforementioned delay time of the mechanism from its above level of quarter of the period of the oscillatory period T, i.e., t=T/4, as described below.

As an example, let the initial positioning of the link member 563 assembly of the mechanical delay mechanism gear 466 be as shown with dotted lines in FIG. 29 and indicated by the numeral 573. The applied activation acceleration is also considered to have rotated the gear 466 in the clockwise direction as was previously described to the indicated positioning of the link member 563 assembly shown in solid lines, at which point the gear 466 is released. With this resting position of the gear 466 of the oscillatory mechanical delay mechanism, once the gear 466 is released, it is rotationally accelerated in the counterclockwise direction until it reaches its peak velocity when the link member assembly reaches the position 573 during a quarter of the period of oscillation T, equation (7), of the oscillatory mechanical delay mechanism. The gear 466 would then continue to rotate in the counterclockwise direction, while decelerating by the torque provided by the winding of the torsion spring 470, FIG. 22. The rest position 573 of the link member assembly is positioned such that as the gear 466 continues to rotate in the counterclockwise direction, when its tip 566 engages the tip 567 of the striker release member 523, the mechanical delay mechanism has enough kinetic energy to rotate the striker release member enough in the clockwise direction to release the striker member 520, FIG. 28, upon impact.

Then, as was described previously, following the release of the gear 466, the gear 466 would begin to be accelerated in the counterclockwise direction to its peak velocity as it reaches to the position 573, FIG. 29, during one quarter of the period T of a full cycle of the oscillatory mechanical delay mechanism, FIG. 22, equation (7). The gear 466 is then decelerated in the counterclockwise direction, but while it has enough velocity, i.e., while the oscillatory mechanical delay mechanism has enough rotational kinetic energy, the tip 566 of its link member 563 impacts the tip 567 of the striker release member 523, rotating it in the clockwise direction and releasing the striker member 520, FIG. 28, causing the inertial igniter to be initiated as was previously described. The amount of time that it takes for the link member 563 assembly to rotate from its position 573 to the point of striking the tip 567 of the striker release member 523 is less than one quarter of the period of oscillation T of a full cycle of the oscillatory mechanical delay mechanism, FIG. 22, since the gear is still rotating in the counterclockwise direction with certain rotational velocity. As a result, the total delay time t, produced by the mechanical delay mechanism, i.e., the time taken from the time of releasing of the gear 466 until the striker release member is impacted can be seen to be in the range of T/4<t<T/2, i.e., greater than the gear 466 resting positioning of FIG. 26.

The total delay time t, produced by the mechanical delay mechanism, i.e., the time taken from the time of releasing of the gear 466 until the striker release member is impacted can be increased to a larger portion of the period T of one cycle of the mechanical delay mechanism of FIG. 22 oscillation. This can be achieved by the following modification of the mechanical delay and striker and striker release mechanism assembly as shown in the schematic of FIG. 26, which is shown in the schematic of FIG. 30.

The side view “H” of the modified initiator striker mechanism component 402 of the inertial igniter embodiment 400 of FIG. 19, together with the striker releasing rotationally oscillating gear member are shown in the schematic of FIG. 30. All components shown in the schematic of FIG. 30 are identical to those of the components shown in the schematic of FIG. 26 and are indicated by the same numerals, except for the striker release member 574 (523 in FIG. 26) and the gear 466 attached link member 575 (563 in FIG. 26), and their related components as described below.

In the modified initiator striker mechanism component 402 of the inertial igniter embodiment 400 of FIG. 19 shown in FIG. 30, the striker release member 574 is similarly attached to the structure 406 by the rotary joint 576 via the support member 577. The preloaded torsion spring 526 of the striker member 520 is similarly shown to bias the tip 527 of the striker member against the tip 578 of the striker release member 574 in the pre-activation state of the inertial igniter embodiment 400. A lightly preloaded compressive spring 579 is also provided to bias the striker release member against the striker member tip 527 as shown in FIG. 30. The compressive spring 579 is attached to the structure 406 of the inertial igniter on one end and to the striker release member 574 on the other end as can be seen in FIG. 30.

As can be seen in the schematic of FIG. 30, a member 580 (562 in FIG. 26) is fixedly attached to the side surface of the gear 466 (behind the gear as viewed in FIG. 30 and clearing the gear teeth), to which a link member 575 (563 in FIG. 26) is attached by the rotary joint 581 (564 in FIG. 26). The link member 575 in biased against the stop 582 (565 in FIG. 26), which is fixedly attached to the member 580, by a preloaded torsion spring (not shown) provided at the joint 581. In the configuration shown in the schematic of FIG. 30, the gear 466 is rotating in the counterclockwise direction as shown by the arrow 583 and the tip 584 (566 in FIG. 26) of the link member 575 is about to strike the tip 585 (567 in FIG. 26) of the striker release member 523. The operation of this modified initiator striker mechanism component 402 and the inertial igniter embodiment 400 of FIG. 19 are described below.

Considering that in the schematic of FIG. 30, the gear member 466 is in its rest position, i.e., before the inertial igniter embodiment 400 of FIG. 19 is subjected to any acceleration in the activation direction. It is appreciated that in this configuration of the inertial igniter mechanisms, the torsion spring 470 of FIG. 22, 494 of FIGS. 23 and 25, and 505 of FIG. 24 are in their free (unloaded) state. Now when the device to which the inertial igniter is attached is subjected to the activation acceleration, then the inertially actuating link members of the “spring winding component” 401 or 432 of FIGS. 20A and 21A, respectively, that is being used would begin to rotate the gear member 466, FIG. 30, in the clockwise direction as viewed in the schematic of FIG. 30

In FIG. 31, the gear member 466 and the striker release member 574 are redrawn. In this illustration, the arrow 586 shows the direction of inertially actuating link members of the “spring winding component” rotating the gear member 466 and winding the torsion spring 526 of the mechanical delay component 461 of the inertial igniter, FIG. 19, and the arrow 587 shows the (counterclockwise) direction of the gear member 466 rotation once it is released by the “spring winding rotation” mechanism 465, FIG. 22.

Now, consider the scenario in which when the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is subjected to the activation acceleration, and that the inertially actuating link members of the “spring winding component” used in the inertial igniter, i.e., “spring winding component” 401 or 432 of FIGS. 20A and 21A, respectively, would rotate the gear member 466, FIG. 31, in the clockwise direction from its position shown in FIG. 30 to the position shown in FIG. 31, where the positioning of the link member 575 is indicated by the numeral 600. It is appreciated that as can be viewed in the schematics of FIGS. 30 and 31, the gear 466 is thereby rotated around 270 degrees in the clockwise direction as indicated by the arrow 586, at which point the gear is released by the “spring winding rotation” mechanism 465 as was previously described, FIG. 22D. During the clockwise rotation of the gear 466, the torsion spring of the mechanical delay component 461, i.e., the torsion spring 470 of FIG. 22, or 494 of FIGS. 23 and 25, or 505 of FIG. 24, whichever is used in the inertial igniter, is also wound the same amount.

In the following description of the operation of the inertial igniter embodiment 400 of FIG. 19, the mechanical delay component of FIG. 22 is used to describe the operation of the inertial igniter up to the point of its percussion primer initiation. It is appreciated that the same process also applies when other above mechanical delay components are used in the construction of the inertial igniter.

Now, when the gear member 466 is released from its positioning of FIG. 31, i.e., the positioning of the link member 575 assembly as indicated by the numeral 600, the gear member (and other rotating members of the mechanical delay mechanism) is rotationally accelerated by the torque of the wound torsion spring 470, FIG. 22, in the counterclockwise direction as viewed in the schematics of FIGS. 30 and 31, and as shown by the direction of the arrow 587, until the link member 575 assembly reaches to its positioning in light color and indicated by the numeral 601, at which point the gear 466 and other rotating components of the oscillatory mechanical delay mechanism have reached their peak rotational velocity, at which point the entire potential energy stored in the torsion spring 470 has been converted to the kinetic energy of the oscillatory mechanical delay mechanism system (neglecting friction and other sources of energy loss). The gear member 466 would then begin to be decelerated by the winding of the torsion spring 470 until it would come to a stop around its positioning shown by light color and indicated by the numeral 602 in FIG. 31, i.e., after around 270 degrees of counterclockwise rotation. It is appreciated that as the link member 575 passes the tip 585 of the striker release member 574, the link 575 is rotated in the clockwise direction relative to the gear 466 until it clears the tip 585 of the striker release member.

It is appreciated that neglecting the usually small friction and other losses, by the time that the link member 575 reaches to is positioning 602, its rotational velocity and therefore the rotational kinetic energy of the oscillatory mechanical delay mechanism has vanished and the gear 466 comes momentarily to a stop. In this configuration of the oscillatory mechanical delay mechanism, the torsion spring 470, FIG. 22, is wound again, but in the opposite direction from the time that the gear 466 was released, with the same amount of stored potential energy. Obviously in practice, some of the initial stored mechanical energy in the torsion spring 470 is lost during its above half a cycle of its oscillation. It is also appreciated that the time t that it takes for the gear 466 to reach the positioning with the link member in the positioning 602 from the time of its release is half the period T, equation (7), of the oscillatory mechanical delay mechanism of FIG. 22, i.e., t=T/2.

Then from the gear positioning with the link member 575 in the position 602, FIG. 31, the gear would rotationally accelerate in the clockwise direction, and gain its maximum rotational velocity when the link member 575 reaches close to its positioning indicate as 601, and the tip 584 of the link member 575 strikes the tip 585 of the striker release member 574 (from below, as viewed in FIG. 31), causing it to rotate in the counterclockwise direction as viewed in the schematic of FIG. 31, thereby causing the tip 578 of the striker release member 574 to disengage the tip 527 of the striker member 520. The striker member is then rotationally accelerated in the counterclockwise direction by the preloaded torsion spring 526. The moment of inertia of the striker member about the axis of rotation of the rotary joint 521 and the preloading level and spring rate of the torsion spring 526 are selected such that the striker member gains enough kinetic energy as its sharp tip 568 strikes the percussion primer 569, as shown in FIG. 32, to reliably initiate it. The ignition flame and sparks would then exit from the opening 570 in the structure of the inertial igniter.

As indicated above, the time t that it takes for the gear 466 to reach the positioning with the link member in the positioning 602 from the time of its release is half the period T, equation (7), of the oscillatory mechanical delay mechanism (system) of FIG. 22, i.e., t=T/2. This is the case since the gear 466 takes a quarter of the period T of one cycle of the oscillatory system to rotate in the counterclockwise from the link member 575 positioning 600 to the positioning 601 (i.e., the oscillatory system initial resting positioning), and it takes another quarter of the period T of the cycle of oscillation for the gear to continue to rotate in the counterclockwise direction, while being decelerated by the winding of the torsion spring 470, FIG. 22, and come to momentary rest as indicated by the positioning 602 of the link member 575. The wound torsion spring 470 would then rotationally accelerate the gear 466 in the clockwise direction (for around 270 degrees) to its peak rotational velocity until the tip 584 of the link member 575 impacts the tip 585 of the striker release member 574 and causes it to release the striker member 520 as previously described, the process which takes another quarter of the period T of one cycle of the oscillatory system. Thus, the total “delay time” generated by the mechanical delay mechanism, i.e., the time passed from the moment of the gear 466 release by the “spring winding rotation” mechanism 465 as was previously described, FIG. 22D, to the moment that the striker release member 574 is struck by the link member 575 to release the striker member 520, becomes around t=3T/4.

It is appreciated by those skilled in the art that the components of the inertial igniter embodiment 400 of FIG. 19, such as the striker release member 523 and 574, FIGS. 26 and 30, respectively, and the striker member 520, FIG. 26, are desired to have their centers of mass at or very close to their rotary joints so that if the device to which they are attached is accelerated in the lateral directions as viewed in FIGS. 26 and 30, the striker member of the inertial igniter is not released, for example by causing the striker release member 523 (574) to be rotated in the clockwise (counterclockwise) direction, thereby releasing the striker member and causing the inertial igniter to initiate.

It is also appreciated by those skilled in the art that when the device to which the inertial igniter 400 of FIG. 19 is attached is subjected to the prescribed inertial igniter activation acceleration level threshold, the units of the “spring winding component” 401 of FIG. 20A or 431 of FIG. 21A that is used in its construction would begin to sequentially actuate and rotate the output shaft (463 in FIG. 20A and 464 in FIG. 21A) of the “spring winding component” until the engaging gear 466, FIGS. 22-25, is released. However, if the prescribed acceleration duration is very short and ends before the engaging gear 466 is released as was previously described, then the “spring winding component” and thereby all other components of the inertial igniter embodiment 400 would reset, i.e., return to their initial configuration.

However, since in the inertial igniter embodiment 400 of FIG. 19 the time that it takes for the units of the “spring winding component” 401 of FIG. 20A or 431 of FIG. 21A to wind the mechanical delay mechanism torsion spring and release the gear 466 is significantly shorter than the prescribed activation acceleration duration, then the gear 466 of the oscillatory mechanical delay mechanism may be released, but the prescribed activation acceleration may cease or fall below the prescribed threshold level before the prescribed duration threshold has been reached. The above disclosed inertial igniter embodiments 400 of FIG. 19 must therefore be provided with the capability of aborting its initiation process once the process of winding the torsion spring of the mechanical delay mechanism, such as spring 470 of FIG. 22, has been completed and the gear 466 has been released if the prescribed activation acceleration level does not persist for the entire prescribed activation duration. Several methods and related designs for providing such a capability to the disclosed inertial igniter embodiment 400 of FIG. 19 are described below.

In addition, in certain munitions applications, it is also highly desirable that if the munition is subjected to a very high acceleration shock loading, for example if it is dropped from a relatively high height that would subject the munition to a “very high G acceleration shock level event” that may even be orders of magnitude higher than the firing acceleration level, then the igniter would be prevented from being activated. In certain such applications, the inertial igniter is required to be rendered non-functional, i.e., would not be initiated even if it is subjected to the prescribed activation acceleration level and duration. In other applications, the inertial igniter may be required to stay functional following such a “very high G acceleration shock level event”, i.e., initiate when subjected to the prescribed activation acceleration level and duration. Methods and related designs for providing such a capability to the disclosed inertial igniter embodiment 400 of FIG. 19 are also described below.

Several methods are herein described that may be used alone or in combination to provide one or both of the above capabilities to the inertial igniter embodiments 400 of FIG. 19, i.e., the capability of aborting the inertial igniter initiation process if the activation acceleration is ceased or drops below its prescribed threshold before its prescribed duration has elapsed, or if the inertial igniter is subjected to a relatively short, i.e., significantly shorter than the prescribed activation acceleration duration, but “very high acceleration” event, i.e., acceleration levels that are significantly higher than the prescribed activation acceleration in the direction of activation acceleration.

The cross-sectional view C-C of FIG. 20A shown in FIG. 20B, which shows the side view of the first inertially actuating link member 407 of the inertial “spring winding component” of the inertial igniter embodiment 400 of FIG. 19 in its pre-activation state is redrawn in FIG. 33A. It is appreciated that as it was described previously, when the inertial igniter is subjected to the activation acceleration in the direction of the arrow 414, the inertial force acting at the center of mass of the inertially actuating link member 407 would begin to rotate the link member 407 in the clockwise direction as viewed in FIG. 33A. As a result, the extended member 420 of the inertially actuating link member 407 would also begin to be displaced downward as viewed in FIG. 33A. In the present method of preventing actuation of the inertially actuating link member 407 (and link members 408 and 409, FIG. 20A), a stop member 588, which is free to displace over the surface 603 provided on the structure 406 of the inertial igniter is provided. The stop member 588 is also provided with a compressive spring 589, which is attached to the stop member 588 on one end and to the structure 406 of the inertial igniter on the other end. In the rest position of the inertial igniter shown in the schematic of FIG. 33A, the stop member blocks downward displacement of the extended member 420, thereby preventing clockwise rotation, i.e., actuation, of the inertially actuating link member 407. The mass of the stop member and the spring rate of the compressive spring 589 are configured such that when the inertial igniter is subjected to an activation acceleration in the direction of the arrow 414 that is at or above the prescribed acceleration threshold, then the stop member is displaced to the right as viewed in FIG. 33A due to the generated inertial force acting on the compressive spring and causing it to deform. The inertially actuating link member 407 (and link members 408 and 409, FIG. 20A) would then be free to begin to perform their actuating functions.

It is appreciated by those skilled in the art that once the acceleration in the direction of the arrow 414 has ceased, the inertial igniter embodiment 400 of FIG. 19 would return (reset) to its initial state.

The cross-sectional view C-C of FIG. 20A shown in FIG. 20B, which shows the side view of the first inertially actuating link member 407 of the inertial “spring winding component” of the inertial igniter embodiment 400 of FIG. 19 in its pre-activation state is also redrawn in FIG. 33B. In this method of preventing actuation of the inertially actuating link member 407 (and link members 408 and 409, FIG. 20A), as can be seen in the schematic of FIG. 33B, a stop mechanism, consisting of a link member 604, which is attached to the structure 406 of the inertial igniter by the rotary joint 605, via the support member 606, is provided. The stop mechanism is also provided with a compressive spring 607, which is attached to the link member 604 on one end and to the structure 406 of the inertial igniter on the other end.

In the rest position of the inertial igniter shown in the schematic of FIG. 33B, the extended end 608 of the link member 604 is positioned not to block downward displacement of the extended member 420 as viewed in FIG. 33B, thereby does not prevent clockwise rotation, i.e., actuation, of the inertially actuating link member 407. The center of mass of the link member 604 is configured to be positioned on the compressive spring 607 side of the rotary joint 605. The center of mass and the mass of the link member 604 and the spring rate of the compressive spring 607 are configured such that when the device to which the inertial igniter is attached is accelerated in the direction of the arrow 414 at a previously described “very high acceleration” event rate, then the link member 604 is rotated by the generated inertial force acting at the center of mass of the link member to rotate it in the counterclockwise direction, thereby positioning the extended end 608 in the path of the extended member 420 of the inertially actuating link member 407 as shown by dashed lines and indicated by the numeral 609, thereby preventing the inertially actuating link member 407 to rotate in the clockwise directions and perform its actuation function. The inertial igniter is thereby prevented from being initiated.

It is appreciated that in certain applications, once the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is subjected to an aforementioned “very high acceleration” event in the direction of the activation acceleration, the inertial igniter is desired to stay non-functional, i.e., that it would stay incapable of being initiated even if it is subjected to the prescribed acceleration level and duration threshold. This capability may be added to the inertially actuating link member 407 (and link members 408 and 409, FIG. 20A), of the inertial “spring winding component” of the inertial igniter embodiment 400 of FIG. 19 shown in FIG. 33B as described below.

As can be seen in the schematic of FIG. 33B, the above goal is accomplished by providing a stop member 636, which in normal conditions is biased against the extended end 608 of the link member 604 by the preloaded compressive spring 638. The preloaded compressive spring 638 is attached to the stop member 636 on one end and to the support member 637, which is fixedly attached to the structure 406 of the inertial igniter, on the other end. Now, when the device to which the inertial igniter is attached is subjected to a “very high acceleration” event in the direction of the arrow 414, as it was previously described, the link member 604 would rotate in the counterclockwise direction, thereby preventing the inertially actuating link member from being rotated in the clockwise direction, thereby preventing the inertial igniter from being initiated. In the meanwhile, the stop member 636 is pushed under the link member 604 as shown by dashed lines and indicated by the numeral 639. As a result, after the “very high acceleration” event has ceased, the link member 604 cannot return to its initial positioning and still blocks clockwise rotation of the inertially actuating link member 407 (and link members 408 and 409, FIG. 20A), and renders the inertial igniter embodiment 400 of FIG. 19 non-functional.

The cross-sectional view E-E of FIG. 21A shown in FIG. 21B, which shows the side view of the first inertially actuating link member 439 of the inertial “spring winding component” of the inertial igniter embodiment 400 of FIG. 19 in its pre-activation state is redrawn in FIG. 34A. The link member 439 is, however, provided with an additional extended member 610 as can be seen in FIG. 34A. It is appreciated that as it was described previously, when the inertial igniter is subjected to the activation acceleration in the direction of the arrow 447, the inertial force acting at the center of mass of the inertially actuating link member 439 would begin to rotate the link member in the clockwise direction as viewed in FIG. 34A. As a result, the extended member 610 of the inertially actuating link member 439 would also begin to be displaced downward as viewed in FIG. 34A. In the present method of preventing actuation of the inertially actuating link member 439 (and link members of the units 433, 434 and 435, FIG. 21A), a stop member 611, which is free to displace over the surface 612 provided on the structure 406 of the inertial igniter is provided. The stop member 611 is also provided with a compressive spring 613, which is attached to the stop member 611 on one end and to the structure 406 of the inertial igniter on the other end. In the rest position of the inertial igniter shown in the schematic of FIG. 34A, the stop member blocks downward displacement of the extended member 610, thereby preventing clockwise rotation, i.e., actuation, of the inertially actuating link member 439. The mass of the stop member 611 and the spring rate of the compressive spring 613 are configured such that when the inertial igniter is subjected to an activation acceleration in the direction of the arrow 447 that is at or above the prescribed acceleration threshold, then the stop member is displaced to the right as viewed in FIG. 34A due to the generated inertial force acting on the compressive spring and causing it to deform. The inertially actuating link member 439 (and link members of the units 433, 434 and 435, FIG. 21A) would then be free to begin to perform their actuating functions.

It is appreciated by those skilled in the art that once the acceleration in the direction of the arrow 447 has ceased, the inertial igniter embodiment 400 of FIG. 19 would return (reset) to its initial state.

The cross-sectional view E-E of FIG. 21A shown in FIG. 21B, which shows the side view of the first inertially actuating link member 439 of the inertial “spring winding component” of the inertial igniter embodiment 400 of FIG. 19 in its pre-activation state is redrawn in FIG. 34A. In this method of preventing actuation of the inertially actuating link member 439 (and link members of the units 433, 434 and 435, FIG. 21A), as can be seen in the schematic of FIG. 34B, a stop mechanism, consisting of a link member 614, which is attached to the structure 406 of the inertial igniter by the rotary joint 615, via the support member 616, is provided. The stop mechanism is also provided with a compressive spring 617, which is attached to the link member 614 on one end and to the structure 406 of the inertial igniter on the other end. In the rest position of the inertial igniter shown in the schematic of FIG. 34B, the extended end 618 of the link member 614 is positioned not to block downward displacement of the extended member 610 as viewed in FIG. 34B, thereby does not prevent clockwise rotation, i.e., actuation, of the inertially actuating link member 439. The center of mass of the link member 614 is configured to be positioned on the compressive spring 617 side of the rotary joint 615. The center of mass and the mass of the link member 614 and the spring rate of the compressive spring 617 are configured such that when the device to which the inertial igniter is attached is accelerated in the direction of the arrow 447 at a previously described “very high acceleration” event rate, then the link member 614 is rotated by the generated inertial force acting at the center of mass of the link member to rotate it in the counterclockwise direction, thereby positioning the extended end 618 in the path of the extended member 610 of the inertially actuating link member 439 as shown by dashed lines and indicated by the numeral 699, thereby preventing the inertially actuating link member 439 to rotate in the clockwise directions and perform its actuation function. The inertial igniter is thereby prevented from being initiated.

It is appreciated that as it was indicated previously, in certain applications, once the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is subjected to an aforementioned “very high acceleration” event in the direction of the activation acceleration, the inertial igniter is desired to stay non-functional, i.e., that it would stay incapable of being initiated even if it is subjected to the prescribed acceleration level and duration threshold. This capability may similarly be added to the inertially actuating link member 439 (and link members of the units 433, 434 and 435, FIG. 21A), of the inertial “spring winding component” of the inertial igniter embodiment 400 of FIG. 19 shown in FIG. 34B as described below.

As can be seen in the schematic of FIG. 34B, the above goal is accomplished by providing a stop member 640, which in normal conditions is biased against the extended end 610 of the link member 439 by the preloaded compressive spring 641. The preloaded compressive spring 641 is attached to the stop member 640 on one end and to the support member 642, which is fixedly attached to the structure 406 of the inertial igniter, on the other end. Now, when the device to which the inertial igniter is attached is subjected to a “very high acceleration” event in the direction of the arrow 447, as it was previously described, the link member 614 would rotate in the counterclockwise direction, thereby preventing the link member 439 from being rotated in the clockwise direction, thereby preventing the inertial igniter from being initiated. In the meanwhile, the stop member 640 is pushed under the link member 614 as shown by dashed lines and indicated by the numeral 643. As a result, after the “very high acceleration” event has ceased, the link member 614 cannot return to its initial positioning and still blocks clockwise rotation of the link member 439 (and link members of the units 433, 434 and 435, FIG. 21A), and renders the inertial igniter embodiment 400 of FIG. 19 non-functional.

It is appreciated by those skilled in the art that another method of preventing initiation of the inertial igniter embodiments 400 of FIG. 19 if the prescribed activation acceleration level threshold does not persist for the prescribed duration or when the inertial igniter is subjected to a aforementioned “very high acceleration” is by preventing the striker release member (e.g., the striker release member 523 of FIG. 27) to be rotated by the mechanical delay mechanism as was previously described (e.g., as shown in FIG. 28 for the release member 523 of FIG. 27) if either of the above conditions are present. Such a method is described below by its application to the inertial igniter striker mechanism component 402 of the inertial igniter embodiment 400 of FIG. 19 shown in FIG. 26.

FIG. 26 shows the side view “H” of the inertial igniter striker mechanism component 402 of the inertial igniter embodiment 400 of FIG. 19, together with the striker releasing rotationally oscillating gear member 466. In FIG. 27, the gear member 466 and the striker release member 523 are redrawn. FIG. 27 is redrawn in FIG. 35A with its modified striker release member 625 (523 in FIG. 27) and the added mechanism that prevents the inertial igniter activation by preventing clockwise rotation of the striker release member if the activation acceleration in the direction of the arrow 624 drops below the prescribed activation acceleration threshold. The added mechanism consists of a stop member 627, which is free to displace over the surface 628 provided on the structure 406 of the inertial igniter is provided. The stop member 627 is also provided with a compressive spring 629, which is attached to the stop member 627 on one end and to the structure 406 of the inertial igniter on the other end. The striker release member 625 modification consists of the addition of an extension member 626 as can be seen in the schematic of FIG. 35A.

It is appreciated that as it was described previously, when the inertial igniter is subjected to the activation acceleration in the direction of the arrow 624, once the gear 466 is rotated in the clockwise direction to wind the torsion spring 470, FIG. 22, of the oscillatory mechanical delay mechanism of the inertial igniter, it is released at certain predetermined positioning, for example at the positioning shown in FIG. 35A. Then in the absence of the stop member 627, the gear 466 is rotationally accelerated in the counterclockwise direction until the tip 566 of its link member 563 impacts the tip 567 of the striker release member and cause it to rotate in the clockwise direction and release the striker member 520, FIG. 26, as shown in FIG. 28.

In the rest position of the inertial igniter shown in the schematic of FIG. 35A, the stop member 627 blocks leftward displacement of the extended member 626, thereby preventing clockwise rotation of the striker release member 625, thereby release of the striker member 520, FIG. 26, and initiation of the inertial igniter as was previously described. The mass of the stop member 627 and the spring rate of the compressive spring 629 are configured such that when the inertial igniter is subjected to an activation acceleration in the direction of the arrow 624 that is at or above the prescribed acceleration level threshold, then the stop member is displaced downward as viewed in FIG. 35A due to the generated inertial force acting on the compressive spring 629 and causing it to deform. The striker release member 625 would then be free to rotate in the clockwise direction and release the striker member 520, FIG. 26, as shown in FIG. 28.

It is appreciated by those skilled in the art that once the acceleration in the direction of the arrow 624 has ceased, the inertial igniter embodiment 400 of FIG. 19 would return (reset) to its initial state.

FIG. 35A with its modified striker release member 625 (523 in FIG. 27) but with an added mechanism that prevents the inertial igniter activation by preventing clockwise rotation of the striker release member if the inertial igniter is subjected to an aforementioned “very high acceleration” event is shown in FIG. 35B. The added mechanism consists of a link member 630, which is attached to the structure 406 of the inertial igniter by the rotary joint 631 via the support member 632. The link member 630 is also provided with a compressive spring 633, which is attached to the link member 630 on one end and to the structure 406 of the inertial igniter on the other end. The link member 630 is also provided with an extended end 634.

In the rest position of the inertial igniter shown in the schematic of FIG. 35B, the extended end 634 of the link member 630 is positioned not to block clockwise rotation of the extended member 626 and therefore the striker release member 625 as viewed in FIG. 35B, thereby does not prevent the release of the striker member 520, FIG. 28, and initiation of the inertial igniter embodiment 400 of FIG. 19. The center of mass of the link member 630 is configured to be positioned on the compressive spring 633 side of the rotary joint 631. The center of mass and the mass of the link member 630 and the spring rate of the compressive spring 633 are configured such that when the device to which the inertial igniter is attached is accelerated in the direction of the arrow 624 at a previously described “very high acceleration” event rate, then the link member 630 is rotated by the generated inertial force acting at the center of mass of the link member to rotate it in the counterclockwise direction, thereby positioning the extended end 634 in the path of the extended member 626 of the striker release member 625 as shown by dashed lines and indicated by the numeral 635, thereby preventing the striker release member 625 to rotate in the clockwise direction and release the striker member 520, FIG. 28. The inertial igniter is thereby prevented from being initiated.

It is appreciated that as it was previously indicated, in certain applications, once the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is subjected to an aforementioned “very high acceleration” event in the direction of the activation acceleration, the inertial igniter is desired to stay non-functional, i.e., that it would stay incapable of being initiated even if it is subjected to the prescribed acceleration level and duration threshold. This capability may also be added to the striker release member 625 of the inertial igniter embodiment 400 of FIG. 19 shown in FIG. 35B as described below.

As can be seen in the schematic of FIG. 35B, the above goal is accomplished by providing a stop member 644, which in normal conditions is biased against the extended end 634 of the link member 630 by the preloaded compressive spring 646. The preloaded compressive spring 646 is attached to the stop member 644 on one end and to the support member 645, which is fixedly attached to the structure 406 of the inertial igniter, on the other end.

Now, when the device to which the inertial igniter is attached is subjected to a “very high acceleration” event in the direction of the arrow 624, as it was previously described, the link member 630 would rotate in the counterclockwise direction, thereby preventing the striker release member 625 from being rotated in the clockwise direction, thereby preventing the inertial igniter from being initiated. In the meanwhile, the stop member 644 is pushed under the link member 630 as shown by dashed lines and indicated by the numeral 647. As a result, after the “very high acceleration” event has ceased, the link member 630 cannot return to its initial positioning and still blocks clockwise rotation of the striker release member 625 and renders the inertial igniter embodiment 400 of FIG. 19 non-functional.

It is appreciated by those skilled in the art that since the above methods of preventing inertial igniters if the activation acceleration drops below the prescribed threshold before its duration threshold has been reached or if the inertial igniter is subjected to an aforementioned “very high acceleration” event, examples of which are shown in FIGS. 33A, 33B, 34A, 34B, 35A, 35B, 36A and become effective at different phases of the inertial igniter embodiment 400 of FIG. 19, then in some applications, more than one method of preventing inertial igniter activation may be employed.

It is appreciated that the above methods to prevent the striker release member 625 illustrated in the schematics of FIGS. 35A and 35B for when the activation acceleration drops below the prescribed threshold level and when the inertial igniter is subjected to a “very high acceleration” event, respectively, may also be applied to the modified mechanical delay, striker and striker release mechanism assembly of FIG. 26, which is shown in the schematic of FIG. 30. However, since the tip 584 of the link member 575 strikes on the lower side surface of the striker release member 574 to rotate it in the counterclockwise direction as shown in the schematic of FIG. 32, the link member is stopped below the striker release member since it is held in place by its activated stop members (627 in FIG. 35A and extended member 634 in FIG. 35B). As a result, the gear 466 and thereby the oscillatory mechanical delay mechanism of the inertial igniter cannot return to its normal pre-acceleration state, i.e., the inertial igniter cannot reset (not considering the cases in which the inertial igniter is to be rendered non-functional following a “very high acceleration” event by the stop member 644, FIG. 35B). The resetting capability may be provided to the inertial igniter embodiment 400 of FIG. 19 with the modified mechanical delay, striker and striker release mechanism assembly of FIG. 30, which is shown in the schematic of FIG. 36A as described below.

In the schematic of the modified mechanical delay, striker and striker release mechanism assembly of FIG. 36A, all the components seen are identical to those of the schematic of FIG. 30, except for the modified design of the slider release member 648 (574 in FIG. 30) and the link member 649 assembly (575 in FIG. 30). The stop member 650 and its compressive spring 651 are also added and function as is described later. The stop member is free to displace down over the guide 678 that is provided on the structure 406 of the inertial igniter.

In the modified mechanical delay, striker and striker release mechanism assembly of FIG. 36A of the inertial igniter embodiment 400 of FIG. 19, the striker release member 648 is similarly attached to the structure 406 of the by the rotary joint 652 via the support member 653. The preloaded torsion spring 526 of the striker member 520 is similarly shown to bias the tip 527 of the striker member against the tip 655 of the striker release member 648 in the pre-activation state of the inertial igniter embodiment 400. The striker release member 648 is also provided with an extended member 672. In the pre-activation state of the inertial igniter shown in the schematic of FIG. 36A, the striker release member 648 has an inclined surface 674 at its tip 673. A lightly preloaded compressive spring 654 is also provided to bias the striker release member against the striker member tip 527 as shown in FIG. 36A. The compressive spring 654 is attached to the structure 406 of the inertial igniter on one end and to the striker release member 648 on the other end as can be seen in FIG. 36A.

The mass of the stop member 650 and the spring rate of the compressive spring 651 are configured such that when the inertial igniter is subjected to an activation acceleration in the direction of the arrow 675 that is at or above the prescribed acceleration level threshold, then the stop member is displaced downward as viewed in FIG. 36A due to the generated inertial force acting on the compressive spring 651 and causing it to deform. The striker release member 648 would then be free to rotate in the clockwise direction and release the striker member 520, as shown in FIG. 28.

As can be seen in the schematic of FIG. 36A, a member 656 (580 in FIG. 30) is fixedly attached to the side surface of the gear 466 (behind the gear as viewed in FIG. 36A and clearing the gear teeth), which is provided with a guide 657, inside which the sliding member 658 is free to displace. The sliding member 658 is held in the position seen in FIG. 36A by a compressive spring 659, which is attached to the sliding member on one end and to the member 656 on the other end. The link member 649 (575 in FIG. 30) is attached by the rotary joint 670 to the sliding member 658. The stop member 671 is provided on the sliding member 658 to prevent counterclockwise rotation of the link member 649 relative to the sliding member 658. The link member 649 in biased against the stop 671 by a preloaded torsion spring (not shown). In the configuration shown in the schematic of FIG. 36A, the gear 466 has already been rotated “spring winding component” of the inertial igniter (401 of FIG. 20A or 431 of FIG. 21A) from its rest (pre-activation) positioning, where link member 649 is about to strike the tip 673 of the striker release member 648 as shown in FIG. 30, by around 270 degrees in the clockwise direction as viewed in FIG. 36A. The operation of the inertial igniter embodiment 400 of FIG. 19 with the modifications of FIG. 36A is described below.

Here, in the rest (pre-activation) state of the modified mechanical delay, striker and striker release mechanism assembly of FIG. 36A, the gear member 466 and the link member 649 (575 in FIG. 30) are considered to be positioned as shown in the schematic of FIG. 30. It is appreciated that in this configuration of the inertial igniter mechanisms, the torsion spring 470 of FIG. 22, 494 of FIGS. 23 and 25, and 505 of FIG. 24 are in their free (unloaded) state. Now when the device to which the inertial igniter is attached is subjected to the activation acceleration in the direction of the arrow 675, then the inertially actuating link members of the “spring winding component” 401 or 432 of FIGS. 20A and 21A, respectively, that is being used would begin to rotate the gear member 466 in the clockwise direction as indicated by the arrow 676.

Now let the schematic of FIG. 36A illustrate the positioning of the gear 466 is, i.e., after having been rotated in the clockwise direction around 270 degrees, and at which point it is released by the “spring winding rotation” mechanism 465, FIG. 22.

Now, consider the scenario in which when the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is subjected to the activation acceleration, and that the inertially actuating link members of the “spring winding component” used in the inertial igniter, i.e., “spring winding component” 401 or 432 of FIGS. 20A and 21A, respectively, would rotate the gear member 466, FIG. 36A, in the clockwise direction from its aforementioned initial positioning to the position shown in FIG. 36A. It is appreciated that as can be viewed in the schematics of FIGS. 30 and 36A, the gear 466 is thereby rotated around 270 degrees in the clockwise direction, at which point the gear is released by the “spring winding rotation” mechanism 465 as was previously described, FIG. 22D. During the clockwise rotation of the gear 466, the torsion spring of the mechanical delay component 461, i.e., the torsion spring 470 of FIG. 22, or 494 of FIGS. 23 and 25, or 505 of FIG. 24, whichever is used in the inertial igniter, is also wound the same amount.

In the following description of the operation of the inertial igniter embodiment 400 of FIG. 19, the mechanical delay component of FIG. 22 is used to describe the operation of the inertial igniter up to the point of its percussion primer initiation. It is appreciated that the same process also applies when other above mechanical delay components are used in the construction of the inertial igniter.

Now, when the gear member 466 is released from its positioning of FIG. 36A, i.e., the positioning of the link member 649 assembly, the gear member 466 and other rotating members of the mechanical delay mechanism are rotationally accelerated by the torque of the wound torsion spring 470, FIG. 22, in the counterclockwise direction as viewed in the schematic of FIG. 36A, until as it was described for the schematic of FIG. 31, the link member 649 assembly reaches to its positioning shown in FIG. 31 in light color and indicated by the numeral 601, at which point the gear 466 and other rotating components of the oscillatory mechanical delay mechanism have reached their peak rotational velocity, and at which point the entire potential energy stored in the torsion spring 470 has been converted to the kinetic energy of the oscillatory mechanical delay mechanism system (neglecting friction and other sources of energy loss).

The gear member 466 would then begin to be decelerated by the winding of the torsion spring 470 until it would come to a stop around its positioning shown by light color and indicated by the numeral 602 in FIG. 31, i.e., after around 270 degrees of counterclockwise rotation. It is appreciated that as the link member 649 passes the tip 673 of the striker release member 648, FIG. 36A, the link 649 is rotated in the clockwise direction relative to the gear 466 until it clears the tip 673 of the striker release member 648.

It is appreciated that neglecting the usually small friction and other losses, by the time that the link member 649 reaches to is positioning 602 shown in FIG. 31, its rotational velocity and therefore the rotational kinetic energy of the oscillatory mechanical delay mechanism has vanished and the gear 466 comes momentarily to a stop. In this configuration of the oscillatory mechanical delay mechanism, the torsion spring 470, FIG. 22, is wound again with the same amount of stored potential energy, but in the opposite direction from the time that the gear 466 was released. Obviously in practice, some of the initial stored mechanical energy in the torsion spring 470 is lost during its above half a cycle of its oscillation. It is also appreciated that the time t that it takes for the gear 466 to reach the positioning with the link member 649 in the positioning 602 shown in FIG. 31 from the time of its release is half the period T, equation (7), of the oscillatory mechanical delay mechanism of FIG. 22, i.e., t=T/2.

Then from the gear positioning with the link member 649, FIG. 36A, in the position 602 shown in FIG. 31, the gear 466 would rotationally accelerate in the clockwise direction and gains its maximum rotational velocity when the link member 649 reaches close to the tip 673 of the striker release member 648.

Now, since the inertial igniter is subjected to an activation acceleration in the direction of the arrow 675 that is at or above the prescribed acceleration level threshold, then the stop member is displaced downward as it was previously described and striker release member 648 is free to rotate in the clockwise direction. Thus, as tip 677 of the link member 649 strikes the surface 674 of the tip 673 of the striker release member 648, it causes the striker release member to rotate in the counterclockwise direction as viewed in the schematic of FIG. 36A, thereby causing the tip 655 of the striker release member 648 to disengage the tip 527 of the striker member 520. The striker member 520 is then rotationally accelerated in the counterclockwise direction by the preloaded torsion spring 526. The moment of inertia of the striker member about the axis of rotation of the rotary joint 521 and the preloading level and spring rate of the torsion spring 526 are selected such that the striker member gains enough kinetic energy as its sharp tip 568 strikes the percussion primer 569, as shown in FIG. 32, to reliably initiate it. The ignition flame and sparks would then exit from the opening 570 in the structure of the inertial igniter.

As indicated previously, the time t that it takes for the gear 466, FIG. 36A, to reach the positioning with the link member 649 in the positioning 602 as seen in FIG. 31 from the time of its release is half the period T, equation (7), of the oscillatory mechanical delay mechanism (system) of FIG. 22, i.e., t=T/2. The wound torsion spring 470, FIG. 22, would then rotationally accelerate the gear 466 in the clockwise direction (for around 270 degrees) to its peak rotational velocity until the tip 677 of the link member 649 impacts the tip 673 of the striker release member 648 and causes it to release the striker member 520 as previously described, the process which takes another quarter of the period T of one cycle of the oscillatory system. Thus, the total “delay time” generated by the mechanical delay mechanism, i.e., the time passed from the moment of the gear 466 release by the “spring winding rotation” mechanism 465 as was previously described, FIG. 22D, to the moment that the striker release member 648 is struck by the link member 649 to release the striker member 520, becomes around t=3T/4.

However, if the acceleration in the direction of the arrow 675 has dropped below the prescribed threshold level before the tip 677 of the link member 649 strikes the tip 673 of the striker release member 648, then the stop member would have returned to its inertial igniter resting positioning shown in FIG. 36A, thereby preventing the striker release member 648 from being rotated in the counterclockwise direction and release the striker member 520. The inertial igniter is thereby prevented from being initiated.

It is also appreciated that as the tip 677 of the link member 649 strikes the surface 674 of the striker release member 648, the torque exerted by the clockwise rotating gear would cause the inclined surface 674 (inclined relative to the direction of displacement of the sliding member 658) would force the sliding member 658 to displace back into the guide 657 against the compressive spring 659, thereby for the tip 677 of the link member 649 to clear the tip 673 of the slider release member 648. The oscillatory mechanical delay mechanism would then oscillate with decreasing amplitude until it would eventually come to rest in its initial, i.e., pre-activation acceleration, state. The inertial igniter embodiment 400 of FIG. 19 would thereby reset to its rest to its initial configuration.

It is appreciated that the modified mechanical delay, striker and striker release mechanism assembly of FIG. 36A, may also be provided with the previously described means of preventing striker release member 648 counterclockwise rotation and releasing of the striker member 520 when the inertial igniter is subjected to an aforementioned “very high acceleration” event. The modified mechanical delay, striker and striker release mechanism assembly of FIG. 36A, but with the added mechanism that prevents the inertial igniter activation by preventing clockwise rotation of the striker release member if the inertial igniter is subjected to an aforementioned “very high acceleration” event is shown in FIG. 36B.

The added mechanism consists of a link member 679, which is attached to the structure 406 of the inertial igniter by the rotary joint 680 via the support member 681. The link member 679 is “L” shaped as can be seen in the schematic of FIG. 36B, and is provided with a mass member 682, which shifts its center of mass to the side of the mass member relative to the rotary joint 680. The link member 679 is also provided with a compressive spring 683, which is attached to the link member 679 on one end and to the structure 406 of the inertial igniter on the other end.

In the rest position of the inertial igniter shown in the schematic of FIG. 36B, the side of the link member 679 that is close to the extended member 672 of the striker release member 648 is positioned not to block counterclockwise rotation of the extended member 672 and therefore the striker release member 648 as viewed in FIG. 36B, thereby does not prevent the release of the striker member 520, and initiation of the inertial igniter embodiment 400 of FIG. 19. The center of mass of the link member 679 is configured to be positioned on the compressive spring 683 side of the rotary joint 680. The center of mass and the mass of the link member 679 and the spring rate of the compressive spring 683 are configured such that when the device to which the inertial igniter is attached is accelerated in the direction of the arrow 675 at a previously described “very high acceleration” event rate, then the link member 679 is rotated by the generated inertial force acting at the center of mass of the link member to rotate it in the clockwise direction, thereby positioning the tip 684 of the link member 679 in the path of the extended member 672 of the striker release member 648 as shown by dashed lines and indicated by the numeral 685, thereby preventing the striker release member 648 to rotate in the counterclockwise direction and release the striker member 520. The inertial igniter is thereby prevented from being initiated.

It is appreciated that as it was previously indicated, in certain applications, once the device to which the inertial igniter embodiment 400 of FIG. 19 is attached is subjected to an aforementioned “very high acceleration” event in the direction of the activation acceleration, the inertial igniter is desired to stay non-functional, i.e., that it would stay incapable of being initiated even if it is subjected to the prescribed acceleration level and duration threshold. This capability may also be added to the striker release member 648 of the inertial igniter embodiment 400 of FIG. 19 shown in FIG. 36B as described below.

As can be seen in the schematic of FIG. 36B, the above goal is accomplished by providing a stop member 686, which in normal conditions is biased against the side of the link member 679 by the preloaded compressive spring 687. The preloaded compressive spring 687 is attached to the stop member 686 on one end and to the support member 688, which is fixedly attached to the structure 406 of the inertial igniter, on the other end.

Now, when the device to which the inertial igniter is attached is subjected to a “very high acceleration” event in the direction of the arrow 675, as it was previously described, the link member 679 would rotate in the clockwise direction, thereby preventing the striker release member 648 from being rotated in the counterclockwise direction, thereby preventing the inertial igniter from being initiated. In the meanwhile, the stop member 686 is pushed under the link member 679 as shown by dashed lines and indicated by the numeral 689. As a result, after the “very high acceleration” event has ceased, the link member 679 cannot return to its initial positioning and still blocks counterclockwise rotation of the striker release member 648 and renders the inertial igniter embodiment 400 of FIG. 19 non-functional.

While there has been shown and described what is considered to be preferred embodiments of the invention, it will, of course, be understood that various modifications and changes in form or detail could readily be made without departing from the spirit of the invention. It is therefore intended that the invention be not limited to the exact forms described and illustrated but should be constructed to cover all modifications that may fall within the scope of the appended claims.

Claims

1. An inertial mechanism comprising: a plurality of rotating members configured to be sequentially activated upon experiencing an activation acceleration greater than a predetermined duration and magnitude, the plurality of rotating members comprising: a first rotating member having a first mass and being rotatable about a first axis between a first activatable position and a first activated position, the first activatable position being such that a first center of mass of the first rotating member is offset from the first axis in a direction perpendicular to a direction of the acceleration, the first rotating member further having a first surface; anda second rotating member having a second mass and being rotatable about a second axis between a second rest position and a second activated position, the second rest position being a position in which the second member cannot be moved into the second activated position from the activation acceleration event, the second rotating member further having a second surface, the first surface engaging the second surface when the first rotating member moves to the first activated position to move the second rotating member from the second rest position to a second activatable position, the second activatable position being such that the second center of mass of the second rotating member is offset from the second axis in the direction perpendicular to the direction of the acceleration.

2. The inertial mechanism of claim 1, further comprising a stop for maintaining the first rotating member in the first activatable position when the first rotating member is at rest.

3. The inertial mechanism of claim 2, further comprising a torsion spring for biasing the first rotating member against the stop.

4. The inertial mechanism of claim 3, wherein a biasing force of the torsion spring is overcome when the first rotating member experiences the activation acceleration event to move the first rotating member from the first activatable position to the first activated position.

5. The inertial mechanism of claim 1, wherein the first surface is a first projection protruding from the first rotating member and the second surface is a second projection protruding from the second rotating member.

6. The inertial mechanism of claim 1, wherein the first rotating member rotates about a first shaft and the second rotating member rotates about a second shaft where the first axis is coincident with the second axis.

7. The inertial mechanism of claim 6, wherein the first rotating member only rotates the first shaft over a first range of motion of the first rotating member from the first activatable position to the first activated position and the second rotating member only rotates the second shaft over a second range of motion of the second rotating member from the second activatable position to the second activated position.

8. The inertial mechanism of claim 6, wherein the first shaft and the second shaft comprise a common shaft.

9. The inertial mechanism of claim 6, wherein the first shaft and the second shaft are separated by a one-way mechanism that transfers rotation of the first shaft to the second shaft in only one direction.

10. The inertial mechanism of claim 6, wherein the second shaft is an output shaft to another mechanism.

11. The inertial mechanism of claim 6, wherein the first and second rotating members have first and second gear surfaces configured to engage with first and second mating gear surfaces to rotate a shaft connected to the first and second gear surfaces, the shaft being an output shaft to another mechanism.

12. The inertial mechanism of claim 11, wherein each of the first and second gear surfaces are connected to the shaft by a one-way clutch that transfers rotation of the first and second gear surfaces to the shaft in only one direction.