Patent Application
20150059725
This invention relates, in general, to compressed gas-powered projectile accelerators, generally known as “air-guns,” irrespective of the type of the projectile, gas employed, scale, or purpose of the device.
Compressed gas-powered projectile accelerators have been used extensively to propel a wide variety of projectiles. Typical applications include weaponry, hunting, target shooting, and recreational (non-lethal) combat. In recent years, a large degree of development and invention has centered around recreational combat, where air-guns are employed to launch non-lethal projectiles which simply mark, rather than significantly injure or damage the target. Between launching projectiles such air-guns are generally loaded and reset to fire when the trigger is pulled, generally referred to as “re-cocking” either by an additional manual action by the operator, or pneumatically, as part of each projectile-accelerating event or “cycle.” These devices may be divided into two categories—those that are “non-regulated” or “inertially-regulated,” and those that are “statically-regulated.”
Non-regulated or inertially-regulated air-guns direct gas from a single storage reservoir, or set of reservoirs that are continuously connected without provision to maintain a static (zero-gas flow) pressure differential between them, to accelerate a projectile through and out of a tube or “barrel.” The projectile velocity is typically controlled by mechanically or pneumatically controlling the open time of a valve isolating the source gas, which is determined by the inertia and typically spring force exerted on moving parts. Examples of manually re-cocked non-regulated or inertially-regulated projectile accelerators are the inventions of Perrone, U.S. Pat. No. 5,078,118; and Tippmann, U.S. Pat. No. 5,383,442. Examples of pneumatically re-cocked non-regulated or inertially-regulated projectile accelerators (this type of projectile accelerator being the most commonly used in recreational combat) are the inventions of Tippmann, U.S. Pat. No. 4,819,609; Sullivan, U.S. Pat. No. 5,257,614; Perrone, U.S. Pat. Nos. 5,349,939 and 5,634,456; and Dobbins et al., U.S. Pat. No. 5,497,758.
Statically-regulated air-guns transfer gas from a storage reservoir to an intermediate reservoir, through a valve which regulates pressure within the intermediate reservoir to a controlled design level, or “set pressure,” providing sufficient gas remains within the storage reservoir with pressure in excess of the intermediate reservoir set pressure. This type of air-gun directs the controlled quantity of gas within said intermediate reservoir in such a way as to accelerate a projectile through and out of a barrel. Thus, for purposes of discussion, the operating sequence or “projectile accelerating cycle” or “cycle” can be divided into a first step where said intermediate reservoir automatically fills to the set pressure, and a second step, initiated by the operator, where the gas from said intermediate reservoir is directed to accelerate a projectile. The projectile velocity is typically controlled by controlling the intermediate reservoir set pressure. Examples of statically regulated projectile accelerators are the inventions of Milliman, U.S. Pat. No. 4,616,622.
More recently, electronics have been employed in both non-regulated and statically regulated air-guns to control actuation, timing and projectile velocity. Examples of electronic projectile accelerators are the inventions of Rice et al., U.S. Pat. No. 6,003,504; and Lotuaco, III, U.S. Pat. No. 6,065,460.
Problems with compressed gas powered guns known to be in the art, relating to maintenance, complexity, and reliability, are illustrated by the following partial list:
Sensitivity to liquid CO2—The most common gas employed by air-guns is CO2, which is typically stored in a mixed gas/liquid state. However, inadvertent feed of liquid CO2 into the air-gun commonly causes malfunction in both non-regulated or inertially regulated air-guns and, particularly, statically-regulated air-guns, due to adverse effects of liquid CO2 on valve and regulator seat materials. Cold weather exacerbates this problem, in that the saturated vapor pressure of CO2 is lower at reduced temperatures, necessitating higher gas volume flows. Additionally, the dependency of the saturated vapor pressure of CO2 on temperature results in the need for non-regulated or inertially regulated air-guns to be adjusted to compensate for changes in the temperature of the source gas, which would otherwise alter the velocity to which projectiles are accelerated.
Difficulty of disassembly—In many air-guns known to be in the art, interaction of the bolt with other mechanical components of the device complicates removal of the bolt, which is commonly required as part of cleaning and routine maintenance.
Double feeding—air-guns known to be in the art typically hold a projectile at the rear of the barrel between projectile accelerating cycles. In cases where the projectile is round, a special provision is required to prevent the projectile from prematurely rolling down the barrel. Typically, a lightly spring biased retention device is situated so as to obstruct passage of the projectile unless the projectile is thrust with enough force to overcome the spring bias and push the retention device out of the path of the projectile for sufficient duration for the projectile to pass. Alternatively, in some cases close tolerance fits between the projectile caliber and barrel bore are employed to frictionally prevent premature forward motion of the projectile. However, rapid acceleration of the air-gun associated with movement of the operator is often of sufficient force to overcome the spring bias of retention device, allowing the projectile to move forward, in turn allowing a second projectile to enter the barrel. When the air-gun is subsequently operated, either both projectiles are accelerated, but to lower velocity than would be for a single projectile, or, for fragile projectiles, one or both of the projectiles will fracture within the barrel.
Bleed up of pressure—Statically-regulated air-guns require a regulated seal between the source reservoir and intermediate reservoir which closes communication of gas between said reservoirs when the set pressure is reached. Because this typically leads to small closing force margins on the sealing surface, said seal commonly slowly leaks, causing the pressure within the intermediate reservoir to slowly increase or “bleed up” beyond the intended set pressure. When the air-gun is actuated, this causes the projectile to be accelerated to higher than the intended speed, which, with respect to recreational combat, endangers players.
Not practical for fully-automatic operation—Air-guns which have an automatic re-cock mechanism can potentially be designed so as accelerate a single projectile per actuation of the trigger, known as “semi-automatic” operation, or so that multiple projectiles are fired in succession when the trigger is actuated, known as “fully-automatic” operation. (Typically air-guns that are designed for fully-automatic operation are designed such that semi-automatic operation is also possible.) Most air-guns known to be in the art are conceptually unsuitable for fully-automatic operation in that there is no automated provision for the timing between cycles required for the feed of a new projectile into the barrel, this function being dependent upon the inability of the operator to actuate the trigger in excess of the rate at which new projectiles enter the barrel when operated semi-automatically. Air-guns known to be in the art which are capable of fully-automatic operation typically accommodate this timing either by inertial means, using the mass-induced resistance to motion of moving components, or by electronic means, where timing is accomplished by electric actuators operated by a control circuit, both methods adding considerable complexity.
Difficult manufacturability—Many air-guns known to be in the art, particularly those designed for fully automatic operation, are complex, requiring a large number of parts and typically the addition of electronic components.
Stiff or operator sensitive trigger pull—The trigger action of many non-electronic air-guns known to be in the art initiates the projectile accelerating cycle by releasing a latch obstructing the motion of a spring biased component. In many cases, since the spring bias must be quite strong to properly govern the projectile acceleration, the friction associated with the release of this latch results in an undesirably stiff trigger action. Additionally, this high friction contact results in wear of rubbing surfaces. Alternatively, in some cases, to reduce mechanical complexity and circumvent this problem, the trigger is designed such that its correct function is dependent upon the technique applied by the operator, resulting in malfunction if the operator only partially pulls the trigger through a minimum stroke.
High wear on striking parts—In many air-guns known to be in the art, particularly those designed for semi-automatic or fully-automatic operation, the travel of some of the moving parts is limited by relatively hard impact with a bumper. Additionally, in many cases, a valve is actuated by relatively hard impact from a slider. The components into which the impact energy is dissipated exhibit increased rates of wear. Further, wear of high impact surfaces in the conceptual design of many air-guns known to be in the art make them particularly un-adaptable to fully-automatic operation.
Contamination—Many of the air-guns known to be in the art require a perforation in the housing to accommodate the attachment of a lever or knob to allow the operator to perform a necessary manipulation of the internal components into a ready-to-fire configuration, generally known as “cocking.” This perforation represents an entry point for dust, debris, and other contamination, which may interfere with operation.
In another aspect of the present invention, in lieu of direct connection of the valve passage and the chamber, the valve and chamber can be connected indirectly by being both connected to a distribution bus, or gas distribution passage, parallel to the bolt bore and valve passage, which simultaneous allows much greater flexibility of the overall configuration while providing a simple means of distributing gas to other functions such as allowing a simple interface with a passage directing gas to a jet that assists in the introduction of projectiles into the barrel. Additionally, this gas distribution passage provides a simple means of controlling flow to the jet by facilitating the incorporation of a throttling screw at the intersection with the passage communicating gas to the jet.
In another embodiment of the present invention, a valve locking feature is provided, whereby force is applied to hold the valve open during the filling of the intermediate reservoir, and then releases the valve body thereafter, reducing the amount of gas pressure required to hold the valve closed during completion of the projectile acceleration cycle. Additionally, because the valve opening force is supplemented by the locking force, the valve spring can be of light design, resulting in an ultra-light trigger pull. In addition, the valve slider diameter can be increased without increasing the spring force acting on the valve slider (with which, through friction, the trigger force scales), thereby allowing the use of larger, more robust seals. Both pneumatic and mechanical techniques to accomplish valve locking are herein described, which can be implemented individually or in combination.
It is desirable in many applications to minimize the length of projectile accelerator barrels. In another embodiment of the present invention, the bolt and breech are designed to allow the replacement a bumper with a stationary (not moving with the bolt) combined bumper and seal, thereby eliminating the need for the front bolt seal and allowing the shortening of the bolt and passage in which it slides, and thereby the overall device, by the length along which the seal slides. When not in operation, with no pressure applied within the chamber formed ahead of the step in the bolt diameter and corresponding step in the breech bore, the pressure of the bolt resting against the combined seal and bumper under the force of the bolt spring will maintain a ready seal between the bolt and breech, which will be sustained during operation as the pressure applied by the bolt is replaced by gas pressure, as the bolt moves rearward, sliding within the combined bumper and seal.
In many applications it is desirable for the first projectile to be fired as quickly as possible following a pull of the trigger, to minimize time for accidental perturbation of aiming and movement of the target during the time for the compressed gas-powered projectile accelerator action to be complete. Thus, it will be advantageous to have the capability to adjust the first cycle to be faster than subsequent cycles. A method to accomplish these is herein detailed, where a second throttling point at the upstream end of a chamber, in turn upstream of the flow control throttling screw, can be used to allow gas accumulated between cycles within the chamber to fill the intermediate chamber faster on the first cycle than subsequent cycles.
The present application provides several methods for the incorporation of a cocking mechanism into the compressed gas-powered projectile accelerator described therein. A novel approach, described herein, embodies a complete cocking system within a plug closing the rear of the valve bore, thereby allowing the cocking capability to contained as a discreet, self-contained module. Further, one embodiment disclosed herein comprises a single piece valve slider comprising of a rear section incorporating the gas seals of the valve and a front portion providing an open cavity partially containing the valve spring and a step by which the sear can latch the valve slider in a non-operating position between cycle. A modification to the valve to include a counter spring can, however, allow the valve slider to be divided into two separate pieces, one acting solely as a valve, and the other containing the velocity control spring and interacting with the sear. So doing simplifies manufacture, and allows the valve to be constructed as a separate module from the remainder of the housing, which is advantageous in allowing a wider range of materials (some of which being unsuitable for use on a larger section of the housing due to weight, but having desirable qualities for use on the valve housing).
One embodiment disclosed herein describes a “dynamically-regulated” compressed gas-powered projectile accelerator which fills an intermediate reservoir as an integral part of, and at the beginning of, each projectile accelerating cycle. The cycle is initiated by the operator, preferably by the action of a trigger, which causes the filling of the intermediate reservoir by compressed gas. The second step of the cycle where the projectile is accelerated is then automatically activated when the pressure reaches a design threshold. In so doing, the filling of the intermediate reservoir may be used not only to regulate the projectile velocity, but the time of each cycle, providing numerous advantages.
In one embodiment, a gas communicated into a chamber that applies pressure to the valve body (therein denoted the “valve slider”) closes the valve when a design pressure reaches a sufficient level to overcome a spring biasing the valve to open. During venting of the gas into the barrel to accelerate the projectile, however, the device relies partially on the bolt inertia and pressure drop through the gas flow path into the barrel (through a hole or slot connecting to the breech and through the hollow bolt) to hold the valve closed until the firing cycle is complete, and an optional throttling screw is described to enable tuning of a flow restriction governing this pressure drop. This causes some loss of efficiency, in preventing full use of the gas to accelerate the projectile. While use of a stiff bolt spring can minimize the dependence upon the bolt inertia and flow frictional losses to hold the valve closed during venting, the added loading subjects adjoining components to additional wear.
Alternatively, dependence upon the bolt inertia and flow losses to hold the valve closed during venting can be avoided by the addition of a valve locking feature, which first applies force to hold the valve open during the filling of the intermediate reservoir, and then releases the valve body thereafter, reducing the amount of gas pressure required to hold the valve closed during completion of the projectile acceleration cycle. Additionally, because the valve opening force is now supplemented by the locking force, the valve spring can be of arbitrarily low stiffness, resulting in an ultra-light trigger pull. Further, the valve slider diameter can be increased without increasing the spring force acting on the valve slider (with which, through friction, the trigger force scales), thereby allowing the use of larger, more robust seals. Both pneumatic and mechanical techniques to accomplish valve locking are herein described, implementable individually or in combination.
In many applications it is desirable for the first projectile to be fired as quickly as possible following a pull of the trigger, to minimize time for accidental perturbation of aiming and movement of the target during the time for the compressed gas-powered projectile accelerator action to complete. A means for adjusting the cycle to a relatively slow rate, and, for adjusting the first cycle to be faster than subsequent cycles is herein detailed, where a second throttling point at the upstream end of a chamber, in turn upstream of the flow control throttling screw of the compressed gas-powered projectile accelerator, can be used to allow gas accumulated between cycles within the chamber to fill the intermediate chamber faster on the first cycle than subsequent cycles.
A unique cocking means is disclosed herein, embodying a complete cocking system within a plug closing the rear of the valve bore, thereby allowing the cocking capability to be added or removed as a discreet, self-contained module.
While some compressed gas-powered projectile accelerators known in the art circumvent some of the above listed problems, all of these and other problems are mitigated or eliminated by the compressed gas-powered projectile accelerator of the present invention. The compressed gas-powered projectile accelerator of the present invention employs a “dynamically-regulated” cycle to avoid the problems associated with both non-regulated or inertially regulated air-guns and statically-regulated air-guns.
The term “dynamically regulated” refers to the fact that the compressed gas-powered projectile accelerator of the present invention, in contrast to air-guns known to be in the art, fills an intermediate reservoir as an integral part of, and at the beginning of, each projectile accelerating cycle. The cycle is initiated by the operator, preferably by the action of a trigger, which causes the filling of the intermediate reservoir by compressed gas. The second step of the cycle where the projectile is accelerated is then automatically activated when the pressure reaches a set pressure threshold. In so doing, the filling of the intermediate reservoir may be used not only to regulate the projectile velocity, but the time of each cycle, making fully automatic operation possible without necessity for inertial or electronic timing. Additionally, since the gas in the intermediate reservoir is used as soon as the pressure reaches the set pressure, the problem of potential bleed-up of the pressure in the intermediate reservoir is eliminated. For further illustration, the type of regulation employed by the compressed gas-powered projectile accelerator of the present invention may be contrasted with that employed by statically-regulated air-guns known to be in the art, where the intermediate reservoir is automatically filled to the set pressure, and the gas stored until the projectile accelerating step of the cycle is triggered by the operator.
This unique cycle additionally maximizes reliability and minimizes wear by allowing all sliding components to rotate freely and requiring no hard impact or high pressure sliding contact between components. The simplicity of assembly allows the housing of the compressed gas-powered projectile accelerator of the present invention to be made as a single piece and the few moving parts can be easily removed for inspection and cleaning.
In another embodiment of the present invention, an additional “gas distribution shaft” is provided, and a valve passage is connected to the gas distribution shaft instead of directly to the chamber. The gas distribution shaft then conducts gas into a passage leading to a chamber between the receiver and bolt diametrical steps, but also can be used to deliver gas at equal pressure to other locations to power additional functions, and can easily incorporate throttling points at either end to allow adjust these functions where throttling provides a desirable measure of control. Because the gas distribution passage makes gas available at any position along the length of the housing, gas delivery to any position along the housing length can be accomplished with minimal impact to geometry.
In another embodiment, gas can be directed to aid in chambering of projectiles by a vertical shaft connecting the gas distribution shaft to a jet in the ball feed assembly, and the geometry of the gas distribution shaft allows a throttling screw to be incorporated at the intersection of the vertical shaft and gas distribution shaft at minimal cost.
In another embodiment, gas can be directed into an annular chamber in the valve passage to firstly pneumatically lock the valve into an open position when a projectile acceleration cycle is initiated, and secondly unlock the valve when gas pressure is being released to accelerate the valve, thereby holding the valve open longer and allowing a greater fraction of the gas to be applied to the acceleration of the projectile before the valve reopens, initiating another projectile acceleration cycle. Alternatively, the same affect can be achieved by a mechanical valve locking cam.
In another embodiment, the bumper located ahead of the step in the bolt diameter can be designed to form a seal between the bolt and the receiver passage step, preferably being an appropriately sized o-ring, thereby eliminating the need for the front bolt o-ring and allowing the receiver passage to be shortened by the length through which the front bolt o-ring would ordinarily travel.
In another embodiment, a second throttling point at the upstream end of the source gas passage can be used to allow gas accumulated between cycles within the source gas passage to cause the chambers ahead of and behind the larger diameter section of the bolt to fill faster on the first cycle that subsequent cycles, thereby allowing the first cycle to be timed differently than subsequent cycles, the first cycle primarily being controlled by the throttling point closest to the valve passage, and subsequent cycles primarily being controlled by the more upstream throttle point.
In another embodiment, the ability to cock the compressed gas-powered projectile accelerator can be accomplished by the addition of a discreet cocking assembly, said cocking assembly being a self-contained component which can provide the optional capability to manually cock the unit without a cocking assembly having to be built into the valve or housing.
In another embodiment, a discreet valve module has been devised where the slider can be divided into two parts, and the valve made as a separate component from the main housing, facilitating manufacture, interfacing and fabrication of connecting passages, and use of alternate construction materials from the housing. The valve module can also incorporate a cocking feature to make an entirely self-contained, sealed valve/cocking assembly.
In another embodiment, an additional “gas distribution passage” is employed, and a valve passage connected to the gas distribution shaft rather than directly to said chamber. Said gas distribution passage then conducts gas into a passage leading to said chamber between the breech and bolt diametrical steps, but also can be used to deliver gas at equal pressure to other locations to power additional functions, and can easily incorporate throttling points at either end to allow adjustment of these functions where throttling provides a desirable measure of control. Because the gas distribution passage makes gas available at any position along the length of the housing, gas delivery to any position along the housing length can be accomplished with minimal impact to geometry as a specific example, gas can be directed to aid in chambering of projectiles by a vertical shaft connecting the gas distribution shaft to a jet in the ball feed assembly, and the geometry of the gas distribution shaft facilitates the incorporation of a throttling screw at the intersection of the vertical shaft and gas distribution passage.
In another embodiment, gas can be directed into an annular chamber in the valve passage to firstly pneumatically lock the valve into an open position when a projectile acceleration cycle is initiated, and secondly unlock the valve when gas pressure is being released to accelerate a projectile, thereby holding the valve open longer and allowing a greater fraction of the gas to be applied to the acceleration of the projectile before the valve reopens, initiating another projectile acceleration cycle. Alternatively, the same affect can be achieved by a mechanical valve locking cam.
In another embodiment, the bumper located ahead of the step in the bolt diameter can be designed to form a seal between the bolt and the breech wall, preferably being an appropriately sized o-ring, thereby eliminating the need for the front bolt seal and allowing the receiver passage to be shortened by the length through which the front bolt seal would ordinarily travel.
In another embodiment, a second throttling point at the upstream end of the source gas passage can be used to allow gas accumulated between cycles within the source gas passage to cause the chambers ahead of and behind the larger diameter section of the bolt to fill faster on the first cycle that subsequent cycles, thereby allowing the first cycle to be timed differently than subsequent cycles, the first cycle primarily being controlled by the throttling point closest to the valve passage, and subsequent cycles primarily being controlled by the more upstream throttle point.
In another embodiment, the ability to cock the compressed gas-powered projectile accelerator can be accomplished by the addition of a discreet cocking assembly, the cocking assembly being a self-contained component which can provide the optional capability to manually cock the unit without a cocking assembly having to be built into the valve or housing.
In another embodiment, a discreet valve module has been devised where the slider can be divided into two parts, and the valve made as a separate component from the main housing, facilitating manufacture, interfacing and fabrication of connecting passages, and use of alternate construction materials from the housing. The valve module can also incorporate a cocking feature to make an entirely self-contained, sealed valve/cocking assembly.
A preferred embodiment of a compressed gas-powered projectile accelerator of the present invention is here and in Figures disclosed. For clarity, within this document all reference to the top and bottom of the compressed gas-powered projectile accelerator will correspond to the accelerator as oriented in
A housing 1, preferably made of a single piece, shown in the Figures in the preferred shape of a pistol which is penetrated by hollow passages which contain the internal components.
A preferably cylindrical receiver passage 2 forms a breech 3 and barrel 4, the latter being preferably extended by the addition of a tubular member, hereafter denoted the “barrel extension” 5, which is preferably screwed into the housing 1 or otherwise removably attached. The barrel 4 is intersected by a projectile feed passage 6 into which projectiles are introduced from outside the housing 1. The projectile feed passage 6 may meet the barrel 4 at an angle but preferably may be at least partially vertically inclined to take advantage of gravity to bias projectiles to move into the barrel 4; conversely an alternate bias, such as a spring mechanism may be employed. The projectile feed passage 6 may connect such that its center axis intersects the center axis of the barrel 4, or, as shown in the examples in the Figures, the projectile feed passage 6 center axis can be offset from the center axis of the barrel 4, as long as the intersection forms a hole sufficiently sized for the passage of projectiles from the projectile feed passage 6 into the barrel 4. Also, the breech 3 diameter may optionally be slightly less than that of the barrel 4 immediately rearward of where the projectile feed passage 6 intersects the barrel 4 to help prevent projectiles from sliding or rolling rearward, as shown in
Preferably parallel to the receiver passage 2 is a preferably cylindrical valve passage 8 of varying cross section which is connected to the breech 3 by a gas feed passage 9, a bolt rest-point passage 10, and a rear passage 11. The valve passage 8 is intersected by a source gas passage 12 and a trigger cavity 13, which is perforated in several places to allow extension of control components to the exterior of the housing 1. The source gas passage 12 is preferably valved, preferably by the use of a screw 14, the degree to which partially or completely blocks the source gas passage 12 depending on the depth to which the screw 14 has been adjusted into a partially threaded hole in the housing 1, intersecting the source gas passage 12. Alternatively, the gas feed passage 9 may be similarly valved instead of, or in addition to, the source gas passage 12 to control flow both between the source gas passage 12 and breech 3, and between the source gas passage 12 and valve passage 8. The screw 14 must form a seal with the hole in which it sits, preferably by the use of one or more o-rings in grooves 15. The source gas passage 12 will preferably include an expanded section 16 to minimize liquid entry and maximize consistency of entering gas by acting as a plenum. Gas is introduced through the source gas passage inlet 17 at the base of the housing 1, which may be designed to accept any high pressure fitting. A gas cylinder, which may be mounted to the housing 1, preferably to the base of the housing 1 in front of the optional trigger guard 18 illustrated in
A sectional view from the side of the housing with most internal components removed is shown in
Passages 9, 10, 11 and/or bleed/test ports 19, 20, 21 may be individually optionally valved to control gas flow, preferably by the use of screws, the degree to which partially or completely block the passage or passages 9, 10, and/or 11, and/or bleed/test ports 19, 20, and/or 21, depending on the depth to which the screws have been adjusted into threaded holes appropriately made in the housing 1, intersecting the passage or passages 9, 10, and/or 11 and/or ports 19, 20, and/or 21. The preferred embodiment depicted in the Figures herein includes an exemplary valve screw 26 at the junction between the rear passage 11 and valve passage 8.
Referring now to
Alternate configurations of these components are shown in detail in
A partially hollow slider or “valve slider” 39 matching the shape of the valve passage 8 as shown in
A preferably removable hollow valve passage cap 43, preferably screwed into the housing 1, traps an optional bumper or “valve bumper” 44 which protects the valve passage cap 43 from wear by contact with the valve slider 39 and vice-versa. A spring or “valve spring” 45 within the valve passage 8, which may be accepted partially within the valve slider 39, and valve passage cap 43, pushes against the valve slider 39 and against a screw 46 preferably threaded inside of the valve passage cap 43, the position of which may be adjusted to increase or decrease tension in the spring 45, thereby adjusting the operating pressure of the cycle and magnitude of projectile acceleration. An optional internal guide 47 for the valve spring can be added. The valve slider 39 can be held in a forward “cocked” position by a sear 40, which can rotate about and slide on a pivot 48. A spring 49 maintains a bias for the sear 40 to slide forward and rotate toward the valve slider 39. Sliding travel of the sear 40 can be limited by means of a preferably cylindrical sliding cam or “mode selector cam” 50 of varying diameter shown in detail in
A lever or “trigger” 54 which rotates on a pivot 55 can press upon the sear 40, inducing rotation of the sear 40. A bias of the trigger 54 to rotate toward the sear 40 (clockwise in
Semi-Automatic Operation of the Compressed Gas-Powered Projectile Accelerator of the Present Invention is Here Described:
The preferred ready-to-operate configuration for semi-automatic operation is shown in
The trigger 54 is then pulled rearward, pulling the sear 40 downward, disengaging it from the valve slider 39, as shown in
Shown in
Shown in
Shown in
The bolt 28 is then driven forward by now unbalanced pressure and spring forces on its surface, pushing the projectile 61 forward in the barrel 4 and blocking the projectile feed passage 6, preventing the entry of additional projectiles. When the bolt 28 reaches the position shown in
Shown in
Shown in
Under the action of the bolt spring 32, the bolt 28 will continue to move forward, compressing gas within the space ahead of the bolt rear seal 36 in so doing, and, allowing only a small gap by which the gas may escape into the valve passage 8, the bolt 28 will be decelerated, minimizing wear on the bolt bumper 31 and stopping in its preferred resting position, as shown in
When the trigger 54 is released, the action of the trigger spring 56, sear spring 49, and valve spring 45 will return the components to the preferred ready-to-fire configuration, shown in
Fully-Automatic Operation of the Compressed Gas-Powered Projectile Accelerator of the Present Invention is Here Described:
The preferred ready-to-operate configuration for fully-automatic operation is shown in
The trigger 54 is then pulled rearward, pulling the sear 40 downward, disengaging it from the valve slider 39, as shown in
Shown in
Shown in
Shown in
The bolt 28 is then driven forward by now unbalanced pressure and spring forces on its surface, pushing the projectile 61 forward in the barrel 4 and blocking the projectile feed passage 6, preventing the entry of additional projectiles. When the bolt 28 reaches the position shown in
Shown in
When the pressure within the valve passage 8 rearward of the valve slider 39 has been reduced to sufficiently low pressure such that the force induced on the valve slider 39 no longer exceeds that of the valve spring 45, the valve slider 39 will begin to slide rearward. If the trigger 54 has not been allowed by the operator to move sufficiently far forward to allow the sear 40 to interfere with the rearward motion of the valve slider 39, the valve slider 39 will continue to move rearward as described in Step 3, and the cycle will begin to repeat, starting with Step 3. If the trigger 54 has been allowed by the operator to move sufficiently far forward to allow the sear 40 to interfere with the rearward motion of the valve slider 39, the valve slider 39 will push the sear 40 rearward into the preferred resting position and will come to rest against the sear 40 as shown in
Under the action of the bolt spring 32, the bolt 28 will continue to move forward, compressing gas within the space ahead of the bolt rear seal 36 in so doing, and, allowing only a small gap by which the gas may escape into the valve passage 8, the bolt 28 will be decelerated, minimizing wear on the bolt bumper 31 and stopping in its preferred resting position, at which point all components will now be in their original ready-to-fire configuration, shown in
Cocking:
Whereas most compressed gas-powered projectile accelerators known to be in the art require a means of manual cocking, the compressed gas-powered projectile accelerator of the present invention will automatically cock when compressed gas, from a source mounted on any location on the housing 1 or other source, is introduced, preferably through a tube, attached to the source gas passage inlet 17. If the compressed gas-powered projectile accelerator of the present invention is un-cocked (i.e., the valve slider 39 is not resting against the sear 40, but further rearward under the action of the valve spring 45) when compressed gas is introduced through the source gas passage 12, said gas will flow through the source passage 12, valve passage 8, and gas feed passage 9 into the region of the breech 3 ahead of the bolt rear seal 36, and one of the semi-automatic or fully automatic cycles above described will ensue at Step 4, the particular cycle being determined by the position of the mode selector cam 50. The automatic cocking feature reduces potential contamination of the compressed gas-powered projectile accelerator of the present invention because said feature removes the necessity the additional perforation of the housing 1 to accommodate the connection of a means of manual cocking to internal components, which constitutes a common path by which dust and debris may enter the housing 1 of many compressed-gas powered projectile accelerators known to be in the art.
A means of manual cocking may be employed, but should be considered optional to the compressed gas-powered projectile accelerator of the present invention, as the addition of a means of manual cocking will allow the operator to bring the compressed gas-powered projectile accelerator of the present invention into a cocked state without cycling, and, more specifically, silently, without the audible report that will be associated with allowing the compressed gas-powered projectile accelerator of the present invention to automatically cock by completing a cycle. The simplest method of applying a manual cocking mechanism to the compressed gas-powered projectile accelerator of the present invention is shown in detail in
The two examples provided are intended to be illustrative as it is to be appreciated that there are numerous methods by which a means of manual cocking (such as the addition of any appendage to the valve slider 39 which may be manipulated from the housing 1 exterior, particularly by protrusion from the front or rear of the valve passage 8) may be incorporated into the projectile accelerator of the present invention without altering the inventive concepts and principles embodied therein.
Expansion Chamber or Second Regulator in Source Gas Passage 12:
One distinct advantage of this preferred embodiment of the compressed gas-powered projectile accelerator of the present invention is that, because the housing 1 can preferably made from a single piece of material, a feed gas conditioning device can easily be incorporated into the housing 1, preferably inserted into the expanded section of the source gas passage 16, shown in detail in
In
In
Pneumatically Assisted Feed:
In
Alternate Bolt Resting Positions:
While the preferred embodiment of the compressed gas-powered projectile accelerator of the present invention has been shown depicting the preferred resting position of the bolt 28 in its most forward travel position because this takes advantage of the bolt 28 to prevent the entry of more than one projectile into the barrel 4 between cycles, it is to be appreciated that small changes in the configuration of the bolt 28, bumpers 31, 38, and bolt spring 32 can cause the bolt 28 to rest in a different location between cycles without changing the basic operation of the compressed gas-powered projectile accelerator of the present invention. If the bolt spring 32 is placed in front of the larger diameter section of the bolt 28, instead of behind as in
Additional Cavities:
It is to be appreciated that the operating characteristics of the compressed gas-powered projectile accelerator of the present invention may be altered by the addition of supplementary cavities, either within the housing or attachments made to the housing, contiguous in any place with any of the internal passages of the apparatus without altering the inventive concepts and principles embodied therein. These cavities may be of fixed or variable volume. (Operating characteristics can be altered by changing the cavity volume.) An example of a compressed gas-powered projectile accelerator made according to the present invention with the addition of a variable volume is illustrated in
Pneumatic Valve Slider Bias:
It is to be appreciated that the operating characteristics of the compressed gas-powered projectile accelerator of the present invention may be altered such that the bias of the valve slider 39 is induced by the pressure of compressed gas, rather than by a valve spring 45, without altering the inventive concepts and principles embodied therein, as shown in
Electronic Embodiment of the Compressed Gas-Powered Projectile Accelerator of the Present Invention:
It is to be appreciated that the operating characteristics of the compressed gas-powered projectile accelerator of the present invention may be altered by the replacement of the valve and internal trigger mechanism components shown in the non-electronic preferred embodiment with electronic components without altering the inventive concepts and principles embodied therein, as shown in
Alternatively, rather than relying upon the mechanical action of pressure within the valve passage 8 rearward of the solenoid valve slider 87 to push the solenoid valve slider 87 into the closed position, the solenoid valve coil 91 can be de-energized when the set pressure is reached, which can be determined based on timing, or by a signal supplied to the control circuit 95 by a pressure transducer 103 (or other electronic pressure sensor), which can be positioned in communication with the gas behind the solenoid valve slider 87 or in the breech 3 either ahead of or behind the largest diameter section of the bolt 28 (i.e. the intermediate reservoir), as shown in
It is also to be appreciated that additional, optional controls can be incorporated into the control circuit 95 of the preferred electronic embodiment of the compressed gas-powered projectile accelerator of the present invention without altering the inventive concepts and principles embodied therein, such as additional switch 100 positions controlling additional operating modes where the projectile accelerator accelerates finite numbers of projectiles, greater than one, generally known as “burst modes” when the trigger 54 is pulled, as compared to semi-automatic operation, where a single projectile is accelerated per trigger 54 pull, and fully-automatic operation, where projectile acceleration cycles continue successively as long as the trigger 54 remains pulled rearward. Additionally, the timing between cycles can be electronically controlled, and said timing can be made adjustable by the inclusion of an additional control dial in the control circuit 95.
In another embodiment of the present invention, shown in
The barrel 108 may be extended by the addition of a barrel extension 110, which is preferably a tubular member threaded or otherwise attached into/onto barrel 108 at the front of the housing 104. The barrel 108 is in communication with a projectile feed passage 112, which may be defined in part by a projectile feed manifold 114 and further extending within the housing 104. Projectiles 116 are introduced into the breech 106 via the projectile feed passage 112. The projectile feed passage 112 may meet the barrel 108 at any angle whereby projectiles 116 can enter the breech 106, but preferably is at least partially vertically oriented with respect to the housing to take advantage of gravity to bias the projectiles 116 into the barrel 108. A means other than gravity may be employed to bias the projectiles into the housing, such as a spring mechanism. The projectile feed passage 112 may be connected such that its center axis intersects the center axis of the barrel 108, as shown in
Preferably parallel to the barrel 108 and breech 106 is a preferably cylindrical gas distribution passage 118, in communication with the breech 120 via an upper gas feed passage 120, and further in communication with a preferably cylindrical valve passage 122 by a lower gas feed passage 124 and valve locking shaft 126. The gas distribution passage 118 may be closed at the front of the housing 104 by a plug, or, as shown in
A feed-assist shaft 130 extends upwardly into the projectile feed manifold 134, and connects with a feed-assist jet 132. Alternatively, the feed-assist shaft 130 can also be connected to the feed-assist jet 132 by a tube 138 routed externally to the projectile feed manifold 134. The throttling screw 128 controls gas flow between the gas distribution passage 118 and the feed assist shaft 130. More particularly, the degree to which the throttling screw 130 partially or completely blocks the intersection of a vertical feed-assist shaft 130 and the gas distribution passage 118 is dependent upon the depth to which the throttling screw 128 has been threaded into the gas distribution passage 118. Of course, if there is no desire to use the gas from the gas distribution passage 118 to assist feeding projectiles 116, the throttling screw 128, feed-assist shaft 130 and feed-assist jet 132 may be removed.
The gas distribution passage 118, feed-assist shaft 130, and feed-assist jet 132 are shown in the same plane as the barrel 108, breech 106, and valve passage 122 centerlines in
Also for ease of understanding, the gas distribution passage 118 is not depicted extending to the rear of the housing 104 in
The valve passage 122 is also in communication with the breech 106 via a bolt rest-point slot 136. A source gas passage 140 is also in communication with the bolt rest-point slot 136. A trigger cavity 142 may also be in communication with the bolt rest-point slot 136. The trigger cavity 142 is perforated in several places to allow extension of control components to the exterior of the housing 104.
The source gas passage 140 is preferably valved, such as by means of a screw 144, the degree to which partially or completely blocks the source gas passage 140 depending upon the depth to which the screw 144 is threaded into the housing 104 so as to intersect the source gas passage 140. Alternatively, the lower gas feed passage 124 or upper gas feed passage 120, may be similarly valved instead of, or in addition to, the source gas passage 140 to control flow both between the source gas passage 140 and breech 106, and between the source gas passage 140 and valve passage 122. The screw 144 should form a seal with the hole in which it sits, preferably by the use of one or more o-rings in grooves 146.
The source gas passage 140 may include an expanded section 148 to minimize liquid entry and maximize consistency of entering gas by acting as a plenum. Gas is introduced through the source gas passage inlet 150 at the base of the housing 104, which may be designed to accept any high pressure fitting. A gas cylinder acting as a source of compressed gas (not shown), may be mounted to the housing 104, preferably to the base of the housing 104 in front of the optional trigger guard 152 illustrated in
A hollow slider or bolt 154 is slidably disposed within the barrel. The bolt 154 preferably has a cylindrical shape that substantially mates with the cylindrical shape of the barrel 108. The bolt 154 is preferably rotatable within the barrel 108 and breech to minimize wear, and is preferably formed from a single piece. The bolt 154 is slidable within the barrel 108 and breech 106 between a forward or first position and a rearward or second position. The bolt 154 has an aperture therethrough for allowing the passage of gas. The bolt 154 may be adapted to move coaxially about a preferably cylindrical spring guide 156 which may be extended within the aperture of the bolt 154. The spring guide 156 has a hollow space at the forward end communicating with at least one or, as shown, a plurality of purge holes 158 about its circumference. A preferably resilient bolt bumper 160 is attached to the bolt 154 at a point where the bolt 154 changes diameter and meets a narrowed portion of the housing, limiting the bolts 154 forward travel and easing shock in the event of malfunction. The bolt bumper may be an o-ring as shown which acts both as a bumper and as a seal between the bolt 154 and the walls of the breech 106.
A bolt spring 162 surrounds the spring guide 156. The spring guide 156 is mounted to a removable breech cap 166. As illustrated, the spring guide 156 may be held in place by a cylindrical cavity in the cap 166 by means of a step in its diameter, and trapped by a screw 164. A spring guide bumper 168, such as an o-ring, may be placed between the end of spring guide 156 and the breech cap 166.
The bolt 154 and spring guide 156 are shown with o-ring/groove type gas seals 170, 172, 174, to prevent leakage. However, various types of seals may be substituted for the illustrated o-rings. Optionally, an additional o-ring/groove type gas seal 176 may be placed at the front tip of the bolt 154. A cylindrical resilient bumper 178 which may be mounted between the bolt 154 and breech cap 166, partially surrounding the bolt 154 and spring guide 156, to protect the bolt 154 and breech cap 166 in the event of malfunction. An o-ring/groove type gas seal 180 may be placed between the breech cap 166 and the wall of the breech to provide further sealing.
As shown in
The valve slider may be formed having a first enlarged portion 189 adjacent the second end of the of the valve slider 182, and a second enlarged portion 191, forward of the first enlarged portion 189, as shown in detail in
A valve spring 196 located adjacent the first end of the valve passage 122 and, preferably, partially within the valve slider 182. The valve spring is positioned between the valve slider 182 and a valve spring guide 198. The valve spring 196 biases the valve slider 182 toward its second position. The valve spring guide 198 may be held in place by a velocity adjustment screw 200 preferably threaded into the valve passage 122. The position of the screw may be adjusted to increase or decrease tension in the valve spring 196, thereby adjusting the operating pressure of the cycle and magnitude of projectile acceleration. The valve slider 182 may be held in its first position by a sear 184, which can rotate about and slide on a pivot 202. A sear spring 204 maintains a bias for the sear 184 to slide forward and rotate toward the valve slider 182. Sliding movement of the sear 184 can be limited by means of a preferably cylindrical mode selector cam 206 which can slide along an axis parallel to the rotational axes of the sear 184 as previously described.
A trigger 208, which rotates on a pivot 210, is adapted to press upon the sear 184, inducing rotation of the sear 184. A bias of the trigger 208 to rotate toward the sear 184 (clockwise in
It will be appreciated by one skilled in the art that the sliding of an o-ring/groove type rear valve slider seal 188, shown in detail in
Discreet Cocking Module:
As described above, the compressed gas-powered projectile accelerator of the present invention will automatically cock when it is in an uncocked position when gas is supplied from a source of compressed gas to the source gas passage 140. It is also desirable to provide some means of manual cocking. This can be accomplished by the addition of a discrete assembly, shown in
Semi-Automatic Operation of the Compressed Gas-Powered Projectile Accelerator:
The preferred ready-to-operate configuration for semi-automatic operation is shown in
The trigger 208 is then pulled rearward, pulling the sear 184 downward, disengaging it from the valve slider 182. The valve slider 182 may then be biased rearwardly to its second position by the valve spring 196.
Under the force applied by the valve spring 196, the valve slider 182 then slides rearwardly to its second position. It may be stopped by contact of its rear bumper with the cocking assembly housing 222. When the valve slider 182 reaches its second position, it allows gas to enter the gas distribution passage 118 through the lower gas feed passage, flow through the gas distribution passage, and into the region of the breech 106 ahead of the bolt rear seal 172. Compressed gas will necessarily also flow into the region of the valve passage 122 forward of the second enlarged portion 191 of the valve slider 182 adding pressure force to hold the valve slider 182 rearward in addition to the valve spring 196 bias. Simultaneously, the sear 184 is caused to slide forward and rotate (shown clockwise in the drawing) by the sear spring 246, coming to rest against the valve slider 182 and, thus, disengaged from the trigger 208.
The pressure of the gas against the bolt rear seal 172 causes the bolt 154 to slide rearward, until the bolt rear seal 172 passes the front edge of the bolt rest-point slot 136, and reaches a preselected position, opening a flow path, and allowing compressed gas to pass into the bolt rest-point slot 136, the valve passage 122 rearward of the valve slider 182, and the region of the breech 106 behind the bolt 154. A projectile 116 may then enter the barrel 108, aided by gravity or some other force, and may be further aided by the suction induced by the motion of the bolt 154 rearward. Additional projectiles 116 in the projectile feed passage 112 are blocked from entering the barrel 108 by the projectile 116 already in the barrel 108. The combined force of the bolt spring 162 and the pressure behind the bolt 154 bring the bolt 154 to rest, preferably without contacting the breech cap bumper 248 at the rear of the breech 106. The bolt 154 will remain approximately at rest, where its position will only adjust slightly to allow more or less gas through the bolt rest-point slot 136 as required to maintain a balance of pressure and spring forces on it while the pressure continues to increase.
Once the pressure in the valve passage 122 rearward of the valve slider 182 has increased sufficiently to overcome the force of the valve spring 196 on the valve slider 182, the valve slider 182 will be pushed forward until the front valve slider bumper 250 contacts the step due to the change in diameter of the valve passage 122, thereby stopping the flow of compressed gas from the source gas passage 140, and allowing the flow of gas from the region of the breech 106 forward of the bolt rear seal 172 and the region of the valve passage 122 forward of the enlarged portion of the valve slider 182 into the valve passage 122 rearward of the valve slider 182, which is in communication with the region of the breech 106 rear of the bolt 154. The sear 184, under the action of the sear spring 246, will rotate further (clockwise in the drawing) once the smaller diameter section of the valve slider 182 has traveled sufficiently far forward to allow this, coming to rest against the smaller diameter section of the valve slider 182.
The bolt 154 is then driven forward by now unbalanced pressure and spring forces on its rear surface, pushing the bolt 154 and projectile 116 forward in the barrel 108 and blocking the projectile feed passage 112, preventing the entry of additional projectiles 116. When the bolt 154 has moved sufficiently far forward that the spring guide seal 174 enters the increased diameter hollow portion at the rear of the bolt 154, disengaging the spring guide seal 174 from the bolt 154 internal bore, gas flows through the purge holes 158 in the spring guide 156 and through the aperture of the bolt 154, to the rear surface of the projectile 116.
The action of the gas pressure on the projectile 116 will cause it to accelerate through and out of the barrel 108 and optional barrel extension 110, at which time the barrel 108, barrel extension 110, breech 106, valve passage 122 rearward of the valve slider 182, and all communicating passages which are not sealed will vent to atmosphere.
When the pressure within the valve passage 122 rearward of the valve slider 182 has been reduced to sufficiently low pressure such that the force induced on the valve slider 182 no longer exceeds that of the valve spring 196, the valve slider 182 will slide rearward until its 40 motion is restricted by the sear 184. The sear 184 will rest against the front of the trigger 208, and may exert a (clockwise in drawing) torque helping to restore the trigger 208 to its 53 resting position, depending on the design of the position of the trigger pivot 210 relative to the point of contact with the valve slider 182.
Under the action of the bolt spring 162, the bolt 154 will continue to move forward, compressing gas within the space ahead of the bolt rear seal 172 in so doing, and, since there is only a small gap by which the gas may escape into the upper gas feed passage 120, the bolt 154 will be decelerated, minimizing wear on the bolt bumper 160 and stopping in its preferred resting position.
When the trigger 208 is released, the action of the trigger spring 212, sear spring 204, and valve spring 196 will return the components to the preferred ready-to-fire configuration, as in Step 1 above.
Fully-Automatic Operation of the Compressed Gas-Powered Projectile Accelerator:
The preferred ready-to-operate configuration for fully-automatic operation is the same as described above for semi-automatic operation except that the mode selector cam 206 is positioned so as to restrict the forward travel of the sear 184, i.e. with the largest diameter section of the mode selector cam 206 interacting with the sear 184.
The trigger 208 is then pulled rearward, pulling the sear 184 downward, disengaging it from the valve slider 182.
Under the force applied by the valve spring 196, the valve slider 182 then slides rearward, until it is stopped by contact of its rear bumper with the cocking assembly housing 222, allowing gas to flow into the region of the breech 106 ahead of the bolt rear seal 172 and into the region of the valve passage 122 ahead of the enlarged portion of the valve slider 182 (adding pressure force to hold the valve slider 182 rearward in addition to the valve spring 196 bias). The mode selector cam 206 prevents the sear 184 from sliding forward sufficiently far to disengage from the trigger 208.
The pressure of the gas causes the bolt 154 to slide rearward, until the bolt rear seal 172 passes the front edge of the bolt rest-point slot 136, allowing gas into the bolt rest-point slot 136, valve passage 122 rearward of the valve slider 182, rear passage, and region of the breech 106 behind the bolt 154. The projectile 116 enters the barrel 108 either by gravity, a positive bias or a negative pressure, such as the suction induced by the motion of the bolt 154. Additional projectiles 116 in the projectile feed passage 112 are blocked from entering the barrel 108 by the projectile 116 already in the barrel 108. The combined force of the bolt spring 162 and the pressure behind the bolt 154 bring the bolt 154 to rest, preferably without contacting the breech cap bumper 248 at the rear of the breech 106. The bolt 154 will remain approximately at rest, where its position will only adjust slightly to allow more or less gas through the bolt rest-point slot 136 as required to maintain a balance of pressure and spring forces on it while the pressure continues to increase.
Once the pressure in the valve passage 122 rearward of the valve slider 182 has increased sufficiently to overcome the force of the valve spring 196 on the valve slider 182, the valve slider 182 will be pushed forward until the front valve slider bumper 250 contacts the step in the valve passage 122, thereby simultaneously stopping the flow of compressed gas from the source gas passage 140, and allowing the flow of gas from the region of the breech 106 ahead of the bolt rear seal 172 and the region of the valve passage 122 ahead of the enlarged portion of the valve slider 182 into the valve passage 122 rearward of the valve slider 182, which is in communication with the region of the breech 106 behind the bolt 154.
The bolt 154 is then driven forward by the now unbalanced pressure and spring forces acting on it, pushing the projectile 116 forward in the barrel 108 and blocking the projectile feed passage 112, preventing the entry of additional projectiles 116. When the bolt 154 has moved sufficiently far forward that the spring guide seal 36 enters the increased diameter hollow portion at the rear of the bolt 154, disengaging the spring guide seal 36 from the bolt 154 internal bore, gas flows through the purge holes 158 in the spring guide 156 and through the center of the bolt 154, into communication with the rear surface of the projectile 116.
The action of the gas pressure on the projectile 116 will cause it to accelerate through and out of the barrel 108 and barrel extension 4, at which time the barrel 108, barrel extension 4, breech 106, valve passage 122 rearward of the valve slider 182, and all communicating passages which are not sealed will vent to atmosphere.
When the pressure within the valve passage 122 rearward of the valve slider 182 has been reduced to sufficiently low pressure such that the force induced on the valve slider 182 no longer exceeds that of the valve spring 196, the valve slider 182 will begin to slide rearward again. If the trigger 208 has not been allowed by the operator to move sufficiently far forward to cause the sear 184 to interfere with the rearward motion of the valve slider 182, the valve slider 182 will continue to move rearward as described above, and the cycle will begin to repeat. If the trigger 208 has been allowed by the operator to move sufficiently far forward to allow the sear 184 to interfere with the rearward motion of the valve slider 182, the valve slider 182 will push the sear 184 rearward into the preferred resting position and will come to rest against the sear 184.
Under the action of the bolt spring 162, the bolt 154 will continue to move forward, compressing gas within the space ahead of the bolt rear seal 172 in so doing, and, since there is only a small gap by which the gas may escape into the upper gas feed passage 120, the bolt 154 will be decelerated, minimizing wear on the bolt bumper 160 and stopping in its preferred resting position, at which point all components will now be in their original ready-to-fire configuration.
Pre-Chamber to Independently Adjust First Cycle Rate from Subsequent Cycles:
A second throttling point upstream expanded section of the source gas passage 148, can be formed by the addition of a throttling screw 236 with one or more preferably o-ring/groove type seals 238 about its diameter, threaded into a shaft 240 intersecting the source gas passage expanded section 148, such that the degree of occlusion of the source gas passage expanded section 148 is adjustable by the depth to which the throttling screw 236 has been threaded, as shown in
A preferred embodiment can be designed with the volume of the portion of the source gas passage 140, 148 between the throttling 150, 236 sized such that the downstream throttling screw 144 can be adjusted so that steady flow rate is established during the first cycle for a desired range of initial cycle times, thus allowing the position of the downstream throttling screw 144 to primarily adjust the time of the first cycle with all subsequent cycle times determined primarily by the position of the upstream screw 236. Alternatively, similar slowing of the cycle rate can be accomplished with the downstream throttling screw 144 adjusted to be equally or more restrictive than the upstream throttling screw 236; however, in such cases, the initial and ultimately achieved steady flow rates will be dependent on the positions of both throttling 150, 236, rather than the initial flow rate being primarily dependent upon the position of the downstream throttling screw 144 and the steady flow rate being primarily dependent upon the position of the upstream throttling screw 236.
Mechanical Valve Locking:
A roller cam assembly, comprised of a rocker 242, preferably holding a wheel 244 and pin assembly 246 (but it is to be appreciated that the replacement of the wheel 244 and pin 246 with a geometrically similar protrusion of the rocker 242 will not alter the inventive concepts and principles embodied herein), biased to rotate about a pivot 248 toward the valve slider 182 by a roller cam spring 250, there engaging a detent in the valve slider 182 when in the rearmost position can be optionally included to mechanically increase the force required to push the valve slider 182 forward, as illustrated in
Valve Module with Integrated Cocking Button:
An alternate embodiment of the compressed gas-powered projectile accelerator is shown in
The truncated valve slider 182 is biased to move forward under the action of a valve slider/cocking plunger return spring 266 located within a cavity inside the truncated valve slider 182 and retained in position by the cocking plunger 226 sliding within the cavity within the valve slider 182, the rear valve passage 262, and the hollow retaining plug 230. The valve slider/cocking plunger return spring 266, which is less stiff than the valve spring 196, serves only to maintain continuous contact between the valve slider 182 and valve spring cup 264, and maintain a bias for the cocking plunger 226 to move rearward, supplanting the similar cocking spring 244 in the previous embodiment (which did not act on the valve slider 182). As in the previously described embodiment, the truncated valve slider 182 forms preferably o-ring/groove type seals at three places with the walls of rear valve passage 262 and it is to be appreciated that the previously described alternate configurations of the valve slider 182 and valve passage 122 shown in
Cocking is accomplished by depression of the portion of the cocking plunger 226 protruding through the hollow retaining plug 230, firstly causing it to slide forward into contact with the truncated valve slider 182 and subsequently pushing the truncated valve slider 182 and valve spring cup 264 forward with continued depression until the valve spring cup 264 has traveled sufficiently far to allow the sear 184, acting under the bias of the sear spring 246, to rotate clockwise into contact with the valve slider 182, thereby preventing rearward return of the valve spring cup 264 when the cocking plunger 226 is allowed to return to its resting position under the bias of the valve slider/cocking plunger return spring 266 by engaging the rear face of the valve spring cup 264. The valve slider/cocking plunger return spring 266 will also act to maintain the valve slider 182 in a forward position, resting against the valve spring cup 264.
Several views of the valve module are shown in detail in
While the source gas passage 140 may be incorporated into the handle 258, corresponding to its location in the housing 104 of previously described embodiment through a similar interface as between the valve module housing 260 and upper housing 254, an alternate scheme is illustrated in
It is to be appreciated that the seals 270, 274, 286 between the upper housing 254 and valve module housing 260 can be replaced by an alternate sealing scheme such as a single gasket without altering the inventive concepts and principles embodied therein.
The embodiment shown in
In addition to the valve spring cup 264, the valve spring passage 256 contains identical components (velocity adjustment screw 49, valve spring guide 198, valve spring 196) to the front half of the valve passage 122 in the previously described embodiment. Because the valve spring 196 and valve slider/cocking plunger return spring 296 maintain constant contact between the valve spring cup 264 and truncated valve slider 182, the valve spring cup 264 and truncated valve slider 182 move together, and act in the same fashion as the valve slider 182 of the previously described embodiment; thus function of the alternate embodiment illustrated in FIGS. is identical to that of the previously described embodiment for both semi-automatic and fully-automatic operation.
It is understood that the present invention is not limited to the particular embodiments shown and described herein, but that various changes and modifications may be made without departing from the scope and spirit of the invention.
This application is a continuation of U.S. patent application Ser. No. 13/488,067, filed Jun. 4, 2012, issuing as U.S. Pat. No. 8,739,770 on Jun. 3, 2014, which is a continuation of U.S. patent application Ser. No. 11/747,107, filed May 10, 2007, now U.S. Pat. No. 8,336,532 issued Dec. 25, 2012 and a continuation of U.S. patent application Ser. No. 11/654,721, filed Jan. 18, 2007, now U.S. Pat. No. 8,191,543 issued Jun. 5, 2012, both of which are continuations of U.S. patent application Ser. No. 10/656,307, filed Sep. 5, 2003, now U.S. Pat. No. 7,237,545, issued Jul. 3, 2007, which is a continuation-in-part of U.S. patent application Ser. No. 10/090,810, filed Mar. 6, 2002, now U.S. Pat. No. 6,708,685, issued Mar. 23, 2004, the entire contents of all of which are incorporated by reference as if fully set forth herein.
| Number | Date | Country | |
|---|---|---|---|
| Parent | 13488067 | Jun 2012 | US |
| Child | 14293618 | US | |
| Parent | 11747107 | May 2007 | US |
| Child | 13488067 | US | |
| Parent | 11654721 | Jan 2007 | US |
| Child | 11747107 | US | |
| Parent | 10656307 | Sep 2003 | US |
| Child | 11654721 | US | |
| Parent | 10656307 | Sep 2003 | US |
| Child | 11654721 | US |
| Number | Date | Country | |
|---|---|---|---|
| Parent | 10090810 | Mar 2002 | US |
| Child | 10656307 | US |
