Cranking Mechanism

Abstract

A cranking mechanism preferably includes a planetary gear set, a drive shaft, a one way bearing, a clutch assembly, and at least one drive unit. The clutch preferably includes a clutch pressure plate, a flywheel, friction surfaces and at least one friction plate. Each drive unit includes a carrier, a spool and a flywheel. The one way bearing and the clutch assembly are axial on the drive shaft. A pressure locking nut is threaded on to a threaded end of the crank shaft to exert pressure on the clutch assembly. The sun gear is fixed on the drive shaft. The at least one drive unit is axial with the drive shaft, and fixed with the carrier of the planetary gear set. The pressure locking nut is tightened against the clutch assembly to frictionally engage the drive shaft with the at least one drive unit.

Description

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates generally to a cranking mechanism, which utilizes a planetary gear set for ease of use. The present invention may also use a one way bearing to lock rotation of a reel. The present invention may utilize a clutch to control rotation of a spool.

2. Discussion of the Prior Art

Cranking devices typically use a ratchet mechanism to lock tension on a line, string or rope. More recently the use of a clutch and a one-way bearing on a direct-drive cocking mechanism was introduced on an AXE 400 crossbow. This device allowed for the silent cocking and un-cocking of a crossbow by the user, however due to this device being direct drive, it was very difficult for the user to cock the crossbow. As the stored energy increased in the limbs, it was increasingly difficult to wind the cranking mechanism. However, it appears that the prior art does not teach or suggest a cranking mechanism which utilizes a planetary gear set, coupled with a spool, to cock a crossbow. Further, it does not teach the use of a one way bearing and or a clutch, coupled with the planetary gearbox to cock a crossbow.

Accordingly, there is a clearly felt need in the art for a cranking mechanism, which utilizes a planetary gear set coupled with a spool, and may be used with a one-way bearing and use of a clutch mechanism to control rotation of a spool. The use of a planetary gear set provides added mechanical advantage for the user, requiring much less effort to cock the crossbow, or alternatively, allowing for much higher poundage limbs while still having the ability to cock the crossbow.

SUMMARY OF THE INVENTION

The present invention provides a cranking mechanism, which utilizes a planetary gear set coupled with a drive unit to cock a crossbow. In addition, the use of a one-way bearing and clutch assembly may control the rotation of the drive unit used to wind (take-up) and unwind (pay out) an elongated connecting device. Functional properties of a planetary gear set are well known. A planetary gear set includes a sun gear, ring gear, planet gears, and a carrier. The carrier has axles radially positioned that carry the planet gears.

Functional properties of a crank mechanism for the winding and unwinding of the elongated connecting device such as a rope, chord or the like device for pulling a secondary object from a first position to a second position. For the disclosed embodiment, we will disclose based on the following:

A one-way bearing is retained in a first cranking boss extending from a first side of a stock. The sun gear is axial with the drive shaft and fixed to the drive shaft. An outer diameter of a ring gear is retained stationary in a second cranking boss to prevent rotation thereof. The second cranking boss extends from a second side of the stock. The ring gear is axial with the drive shaft and sun gear. Planet gears are radially retained on a carrier such that when the sun gear rotates in a first direction, the planet gears and the sun gear rotate in an opposite or second direction. In this arrangement, the planetary gear set allows for a lower input of force on the drive shaft and sun gear to create a higher output of force on the carrier. For the disclosed embodiment, the carrier may be one of coupled with the spool, or integrated with the spool. A clutch assembly may be coupled with the planetary gear assembly to control the rotation of a spool. The cranking mechanism preferably includes a drive shaft, a one way bearing, a clutch assembly, and a planetary gear set coupled with at least one drive unit and with the drive shaft. The drive shaft includes a first driven end having threads, a length, a diameter, a clutch disc engagement portion, a clutch housing portion and second end fixed with a sun gear. A crank handle may be engaged with a locking pressure nut on the driven end. The one-way bearing is pressed in to a second cranking boss extending from a second side of the stock, and radially fixed with the second crank boss to prevent unwanted rotation of the one way bearing.

The clutch assembly is axial with the drive shaft and one-way bearing, and preferably includes a clutch pressure plate having a friction surface, at least one friction plate, and a flywheel having a friction surface. The flywheel may be fixed to the first side of the spool, or preferably integrated with the spool, wherein the friction surface is adjacent the friction plate. The drive unit includes, which is sized to receive the drive shaft. The drive unit includes the carrier. The carrier includes a second side with pins extending therefrom, which are sized to receive the planet gears. The second side of the carrier acts as a portion of the planetary gear set. The drive unit may be retained by at least one radial bearing for proper axial alignment with the drive shaft and the planetary gear set. The drive unit includes a winding diameter, which is sized for the winding and unwinding of the elongated connecting device to couple the drive unit with a trigger housing or a sled designed to pull a bow string.

A sun gear is axially fixed to a second end of the drive shaft, which is driven by the crank handle on a first end. Axial to the drive shaft is a thrust bearing, which is located between the sun gear and the second side of the spool. The drive unit is axial to the drive shaft, and rotates about the drive shaft. The second side of the drive unit is the carrier for the planet gears. The ring gear of the planetary gear set is stationary and is radial to the drive shaft.

The bowstring-drawing means is engaged with a bowstring when the bowstring is in the un-cocked or at-rest position. As the crank handle is rotated a first direction, a pressure locking nut is tightened to the pressure plate, drawing the drive shaft and all associated parts with it towards the locking pressure nut, where the frictional forces occur between the first and second friction surfaces on the friction plate. The drive shaft is rotated in a first direction, causing rotation of the sun gear in a first direction, which in turn causes rotation of the planet gears, rotating the spool/flywheel in an opposite direction of the pressure plate. Frictional forces of the spool/flywheel and the friction disc cause the clutch assembly to “seize”, due to the first pressure surface rotating in an opposite direction of the second pressure surface, tightening on the friction plate. The sun gear turns the planet gears, the planet gears turn the carrier (spool) to wind the elongated connecting device.

Stored energy in the bow limbs of the crossbow bias the elongated connecting device to pay out, or pull away from the spool. The drive unit and the planetary gear assembly bias the drive shaft and clutch assembly to a lock direction of the one-way bearing and pressure locking nut, such that when the crank handle is not rotated, the stored energy forces the drive unit in the direction of pay-out, however the clutch assembly again seizes and the elongated connecting device will not pay out.

Rotation of the crank handle rotated in a second direction, loosens the pressure locking nut from the pressure plate, and the stored energy causes the rotation of the drive unit in the first direction, creating counter-rotational forces throughout the assembly de-compressing the friction surfaces on the friction plate, wherein the drive unit is allowed to rotate and pays out the elongated connecting device until the crank handle is no longer rotated the second direction. The rotation of the crank handle allows the slippage of the clutch assembly just enough as to allow the drive unit to pay out the elongated connecting device. As soon as the crank handle stops rotating, the stored energy continues to bias the elongated connecting device to force the drive unit and all associated components to rotate against the one-way bearing and the pressure locking nut, automatically tightening the pressure locking nut against the pressure plate, again seizing the clutch assembly.

The one way bearing prevents the clutch housing from reversing direction, eliminating the binding forces of the friction, and unwinding the elongated connecting device.

The added feature of the disclosed invention being integrated with the stock and or frame allows for a more compact, easier to manufacture crossbow cranking device. Further, the use of at least one drive unit coupled to the elongated connecting device simplifies design, uses fewer parts, and is easier to manufacture.

An alternative embodiment of a planetary gearbox assembly provides a more compact mechanism. Fewer components allow for a more economical solution, and expand the versatility of the planetary gearbox assembly. The planetary gearbox assembly is axial to a spool winding surface. A drive shaft includes an integrated sun gear and an integrated flywheel in a solitary component. However, the drive shaft and the flywheel may be fabricated from separate components. A first spool side is rotatably retained on an outer perimeter of a first carrier half. A second spool side is rotatably retained on an outer perimeter of a second carrier half. The first and second carrier halves do not rotate relative to housing on a crossbow frame. A plurality of gear axles extend outward from an inside surface of the second carrier half. The plurality of gear axles are sized to rotatably receive a plurality of planet gears. An internal ring gear 28 is preferably attached to the first and second spool sides with a plurality of fasteners (not shown). A winding surface is formed on an outer surface of the internal ring gear. Rotation of the ring gear is driven by the plurality of planet gears. The ring gear rotates concentric with an axis of the sun gear through rotation of the plurality of planet gears.

The first and second carrier halves are preferably fixed in a housing. The first carrier half is attached to the second carrier half with a plurality of threaded fasteners (not shown) inserted through the first carrier half and threaded into the plurality of gear axles. A nut bore is formed through the first carrier half to receive a compression nut. An axle bore is formed through the second carrier half to receive the drive shaft. The drive shaft is on the same axis as the first and second carriers.

The embodiments of the continuation-in-part application disclose a planetary gear set crossbow cocking assembly that has a more compact side to side width than previous embodiments. The spool winding surface is in vertical alignment with the sun gear, the planet gears, and the ring gear. The sun gear is rotatable on its axis, the ring gear is rotatable on the axis of the sun gear, and the planet gears do not rotate round the sun gear. The planet gears are radially retained in a fixed carrier.

For the current disclosure, the elongated connecting device shall be referred to as a “strap”, and “strap” shall be the simple term used to name any type or composition of materials or substances that operably couple the winding spool and the bowstring latch assembly, and may be wound or unwound from the spool winding surface. The “first crank boss” will now be referred to as a “one-way bearing retainer”.

In addition to the above revisions, due to the functional characteristics of the retainment of the planet gears in a fixed carrier, the former flywheel is now a pressure plate, and the former pressure plate is now the flywheel.

Accordingly, it is an object of the present invention to provide a cranking mechanism, which utilizes a one way bearing to prevent rotation of a spool. It is an object of the invention to provide a cranking mechanism incorporated with the stock and or frame providing at least one drive unit coupled to the elongated connecting device to cock a crossbow. It is a final object of this invention to provide a mechanical advantage to the user by the incorporation of a planetary gear set.

These and additional objects, advantages, features and benefits of the present invention will become apparent from the following specification.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a partial rear perspective view of a cranking mechanism in accordance with the present invention.

FIG. 1A is a partial side perspective view of a cranking mechanism in accordance with the present invention.

FIG. 2 is an exploded perspective view of a cranking mechanism in accordance with the present invention.

FIG. 2A is a partial exploded perspective view of a cranking mechanism in accordance with the present invention.

FIG. 2B is partially exploded perspective view illustrating planet gears rotatably retained on a carrier of a cranking mechanism in accordance with the present invention.

FIG. 2C is a partially exploded view with a drive unit retained on a drive shaft of a cranking mechanism in accordance with the present invention.

FIG. 3 is an exploded perspective view of a cranking mechanism in accordance with the present invention.

FIG. 3A is partially exploded view of a cranking mechanism in accordance with the present invention.

FIG. 4 is a perspective view of an assembled cranking mechanism of in accordance with the present invention.

FIG. 4A is a perspective view of an assembled cranking mechanism with an anti-reverse lever in accordance with the present invention.

FIG. 4B is a perspective view of an assembled cranking mechanism of with a one-way bearing in accordance with the present invention.

FIG. 5 is a partial perspective view of a crossbow with an integrated cranking mechanism of the present invention.

FIG. 5a is a partial perspective view of a crossbow with an integrated cranking mechanism retained in portions of a first cranking boss and a second crank boss of the present invention.

FIG. 6 is a partial perspective view of a crossbow with an integrated cranking mechanism of the present invention.

FIG. 7A is a partial perspective view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 7B is a partial perspective view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 8A is a partial perspective view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 8B is a partial perspective view of a preferred embodiment of a planetary gear set crossbow cocking mechanism with a bowstring latch assembly retainment means in accordance with the continuation.

FIG. 9A is a partial view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 9B is a partial view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 9C is a partial exploded view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 10A is a partial exploded view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 10B is a partial exploded view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 11 is a partial exploded view of a preferred embodiment of a planetary gear set crossbow cocking mechanism in accordance with the continuation.

FIG. 12A is a right side perspective view of an alternative embodiment of a cranking mechanism for a crossbow in accordance with the present invention.

FIG. 12B is a left side perspective view of an alternative embodiment of a cranking mechanism for a crossbow in accordance with the present invention.

FIG. 13A is a partially exploded perspective view of an alternative embodiment of a cranking mechanism for a crossbow in accordance with the present invention.

FIG. 13B is an exploded perspective view of an alternative embodiment of a cranking mechanism for a crossbow in accordance with the present invention.

FIG. 14A is a right side exploded perspective view of an alternative embodiment of a cranking mechanism for a crossbow in accordance with the present invention.

FIG. 14B is a right side partially exploded perspective view of an alternative embodiment of a cranking mechanism for a crossbow in accordance with the present invention.

FIG. 14C is a right side partially exploded perspective view of an alternative embodiment of a cranking mechanism for a crossbow in accordance with the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

With reference now to the drawings, and particularly to FIG. 1, there is shown a partial perspective view of a cranking mechanism 10. The cranking mechanism preferably includes a planetary gearbox assembly 20, a drive axle 24, a clutch assembly 40, a drive unit 30, and an elongated connecting device 61.

With reference to FIG. 4A, the cranking mechanism 10a includes a planetary gear assembly 20, a drive unit 30, the elongated connecting device 61, a crank handle 80, an anti-reverse lever 97 and a ratchet gear 99. The ratchet gear 99 is attached to the drive shaft 24, such that the ratchet gear 99 does not rotate relative to the drive shaft 24. The anti-reverse lever 97 and the ratchet gear 99 only allow the drive shaft 24 to rotate in one direction, unless the anti-rotation lever 97 is released from the ratchet gear 99. The crank handle 80 any suitable drive device.

With reference to FIG. 4B, the cranking mechanism 10b includes a planetary gear assembly 20, a drive unit 30, an elongated connecting device 61, a crank handle 80, and a one-way bearing 44.

With reference to FIGS. 2-4, the cranking mechanism 10 preferably includes a planetary gearbox assembly 20. The planetary gearbox assembly 20 includes a sun gear 21, planet gears 22 a carrier 23, and a planetary gearbox housing 29. The drive shaft 24 is fixed axially with the sun gear 21, and axial with the drive unit 30, clutch assembly 40, and one-way bearing 44.

With reference to FIGS. 5-6, the cranking mechanism 10 has been integrated into the stock of a crossbow 95. An outer diameter of the one-way bearing 44 is retained in a first crank boss 91 of the crossbow stock 95 with a key 44a to prevent rotation of the one-way bearing 44 relative to the first cranking boss 91.

With reference to FIGS. 2a-3a, a clutch assembly 40 includes clutch pressure plate 43, at least one friction plate 42 and a drive unit 30. A first pressure surface 41 is formed on an end of the drive unit 30 and a second pressure surface 47 is formed on an end of the clutch pressure plate 43. The at least one friction plate 42 is retained between the first pressure surface 41 and the second pressure surface 47. The first pressure surface 41 may be on a flywheel 48 coupled with the drive unit 30 or integrated with a spool 31 on a first side of the drive unit 30. For the purposes of this disclosure, the flywheel 48 is the input driving force of a clutch assembly 40, and may be a separate component retained by the spool 31, or totally integrated with the drive unit 30, wherein the drive unit 30, flywheel 48 and first friction surface are preferably one component. The second pressure surface is formed on a first end the clutch pressure plate 43 or integrated with the clutch pressure plate 43. A threaded end 26 is formed on a first end of the drive shaft 24, and a pressure locking nut 45 is sized to receive the threaded end 26.

The cranking mechanism 10 utilizes a planetary gearbox assembly 20 coupled with at least one drive unit 30, and a drive shaft 24. The cranking mechanism 10 may alternately include a one-way bearing 44 to lock unwanted rotation of the drive unit 30. The cranking mechanism 10 may alternately include a one way bearing 44, a clutch assembly 40, and a planetary gearbox assembly 20 coupled with at least one drive unit 30 and with the drive shaft 24. The drive shaft 24 includes the threaded end 26 having, a length, a diameter, a friction plate journaling portion, a clutch assembly journaling portion, a drive unit journaling portion, and a second end 27 coupled with a sun gear 21. With reference to FIG. 1, a contoured opening 49 of the crank handle 80 is sized to receive a contoured outer perimeter of the pressure locking nut 45, such that the pressure lock nut 45 does not rotate relative to the crank handle 80. The threaded end 26 is threadably sized to receive the threads of the pressure locking nut 45.

With reference to FIG. 5a, an outer diameter of the one way bearing 44 is pressed into the first cranking boss 91, and radially fixed relative to the first cranking boss 91 to prevent unwanted rotation of the one way bearing 44 with the key 44a. The clutch assembly 40 preferably includes a clutch pressure plate 43 radially fixed with the one way bearing 44, at least one friction plate 42, and a flywheel 48. With reference to FIG. 2, in another embodiment, a drive unit 30 includes separate components of the flywheel 48, a spool 31 and the carrier 23. The flywheel 48 includes a bore, which is sized to receive the drive shaft 24, a first pressure surface 41 is formed on a first side. The spool 31 includes a bore, which is sized to receive the drive shaft 24, a winding diameter 51 and two side walls 33, 35. The first side wall 33 of the spool 31 is engaged with a second side wall of the flywheel 48. A second side wall 35 of the spool 31 is engaged with the carrier 23.

The carrier 23 includes a second side having a plurality of journaling pins 98 extending outward from a second side and sized to receive a plurality of planet gears 22 that enable the second side of the drive unit 30 to perform as a carrier 23 for the planet gears 22. The carrier 23 including the plurality of journaling pins 98 and the spool 31 may be separate structures or they may be combined to make a single structure. The single structure would be called a spool. The drive unit 30 may be coupled with at least one radial bearing (not shown) for proper alignment with the drive shaft 24 and the plurality of planet gears 22. The spool 31 includes the two opposed side walls 33, 35. The winding diameter 51 is sized for the winding and unwinding of the elongated connecting device 61 to couple the drive unit 30 with a bowstring drawing assembly 100 such as a trigger housing, hooks, a sled, or other means known in the art designed to pull a bow string. A pair grooves 37 are formed in the two opposed side walls 33, 35 to receive an anti-rotation pin 39. The anti-rotation pin 39 is retained in an end of the elongated connecting device 61.

The drive shaft second end 27 is axially coupled with a sun gear 21, which is driven by the crank handle 80. Axial to the drive shaft 24 is a thrust bearing 25, which is located between the sun gear 21 and the second side of the carrier 23. The drive unit 30 is axial to the drive shaft 24, and rotates about the drive shaft 24. The ring gear 28 of the planetary gearbox assembly 20 is stationary relative to the stock 95 and is radial to the drive shaft 24.

We will describe three preferred embodiments: First, a cocking assembly with a planetary gear assembly 20 coupled with the drive unit 31 and the elongated connecting device 61. Second, the planetary gear assembly 20 coupled with the drive unit 30, the elongated connecting device 61, and the one-way bearing 44. Third, the planetary gear assembly 20 coupled with the drive unit 30, the elongated connecting device 61, the one-way bearing 44 and the clutch assembly 40.

When the first preferred embodiment is in use, we describe Operation 1 and Operation 2. Operation one will be the rotation of the drive shaft 24 in a first direction. Operation 2 will be the rotation of the drive shaft 24 in a second direction.

Operation 1: The bowstring-drawing assembly 100 is engaged with a bowstring when the bowstring is in the un-cocked or at-rest position. As the crank handle 80 is rotated in a first direction, the drive shaft 24 is rotated in the first direction, causing rotation of the sun gear 21 the first direction, which in turn causes rotation of the planet gears 22, rotating the drive unit 30 to wind the elongated connecting device 61 on the winding diameter 51.

Stored energy in the bow limbs of the crossbow bias the elongated connecting device 61 to pay out, or pull away from the drive unit 30, the drive unit 30 and the planetary gear assembly 20 bias the drive shaft 24 to rotate in a second direction, however due to the anti-reverse lever 97, the elongated connecting device 61 will not pay out.

After disengagement of the anti-reverse lever 97, the crank handle 80 is rotated in a second direction, the drive shaft 24 is rotated in a second direction, causing rotation of the sun gear 21 in a second direction, which in turn causes rotation of the planet gears 22, rotating the drive unit 30 to un-wind the elongated connecting device 61 from the drive unit 30.

Stored energy in the bow limbs of the crossbow bias the elongated connecting device 61 to pay out, or pull away from the drive unit 30, the drive unit 30 and the planetary gear assembly 20 bias the drive shaft 24 to rotate in the second direction. Due to the disengagement of anti-reverse lever 97, the elongated connecting device 61 will pay out.

When the second preferred embodiment is in use, we describe Operation 1 and Operation 2. Operation one will be the rotation of the drive shaft 24 in the first direction. Operation 2 will be the rotation of the drive shaft 24 in the second direction.

Operation 1: The bowstring-drawing assembly 100 is engaged with a bowstring when the bowstring is in the un-cocked or at-rest position. As the crank handle 80 is rotated in the first direction, the drive shaft 24 is rotated in the first direction, causing rotation of the sun gear 21 in the first direction, which in turn causes rotation of the planet gears 22. The sun gear 21 turns the planet gears 22, the planet gears 22 turn the carrier 23 to wind the elongated connecting device 61 on the winding diameter 51.

Stored energy in the bow limbs of the crossbow bias the elongated connecting device 61 to pay out, or pull away from the drive unit 30. The drive unit 30 and the planetary gear assembly 20 bias the drive shaft 24 to lock direction of the one-way bearing 44, that when the crank handle 80 is not rotated, the stored energy forces the drive unit 30 in the direction of pay- out, however the one-way bearing 44 prevents the elongated connecting device 61 from paying out.

After disengaging the one-way bearing 44, the crank handle 80 is rotated in a second direction, the drive shaft 24 is rotated in the second direction, causing rotation of the sun gear 21 the second direction, which in turn causes rotation of the planet gears 22. The sun gear 21 turns the planet gears 22, the planet gears 22 then turn the carrier 23 to unwind the elongated connecting device 61 from the drive unit 30.

When the third preferred embodiment is in use, we describe Operation 1 and Operation 2. Operation one will be the rotation of the drive shaft 24 in a first direction. Operation 2 will be the rotation of the drive shaft 24 in a second direction.

Operation 1: The bowstring-drawing assembly 100 is engaged with a bowstring when the bowstring is in the un-cocked or at-rest position. As the crank handle 80 is rotated in a first direction, a pressure locking nut 45 is tightened to the pressure plate 43, drawing the drive shaft 24 and all associated parts with it towards the locking pressure nut 45, where the frictional forces occur between the first and second pressure surfaces 41 and 47 on the friction plate 42. The drive shaft 24 is rotated in the first direction, causing rotation of the sun gear 21 in the first direction, which in turn causes rotation of the planet gears 22, rotating the first friction surface 41 in an opposite direction of the second friction surface 47. Frictional forces cause the clutch assembly 40 to “seize”, due to the first pressure surface 41 rotating an opposite direction of the second pressure surface 47, tightening on the friction plate 42. The sun gear 21 turns the planet gears 22, the planet gears 22 then turn the carrier 23 to wind the elongated connecting device 61 on the winding diameter 51.

Stored energy in the bow limbs of the crossbow bias the elongated connecting device 61 to pay out, or pull away from the drive unit 30, the drive unit 30 and the planetary gear assembly 20 bias the drive shaft 24 and clutch assembly 40 to the lock a direction of the one-way bearing 44 and the pressure locking nut 45, such that when the crank handle 80 is not rotated, the stored energy forces in the drive unit 30, because the clutch assembly 20 has become seized to prevent rotation of the drive unit 30 which prevents pay out of the elongated connecting device 61.

Operation 2: Rotation of the crank handle 80 in a second direction, loosens the pressure locking nut 45 from the pressure plate 43, and the stored energy causes the rotation of the drive unit 30 in the first direction, creating counter-rotational forces throughout the assembly and de-compressing the friction surfaces 41 and 47 on the friction plate 42, wherein the drive unit 30 is allowed to rotate and pays out the elongated connecting device 61 until the crank handle 80 is no longer rotated in the second direction. The rotation of the crank handle 80 allows slippage of the clutch assembly 40 just enough as to allow the drive unit 30 to pay out the elongated connecting device 61. As soon as the crank handle 80 stops rotating, the stored energy continues to bias the elongated connecting device 61 to force the drive unit 30 and all associated components to rotate against the one-way bearing 44 and the pressure locking nut 45, automatically tightening the pressure locking nut 45 against the pressure plate 43, seizing the clutch assembly 40, thus preventing unwanted rotation of the drive unit 30.

The added feature of the cranking mechanism 10 being integrated with the stock and or frame allows for a more compact, easier to manufacture crossbow cranking device. Further, the use of at least one drive unit 30 coupled to an elongated connecting device 61 simplifies design, uses fewer parts, and is easier to manufacture. The present invention may be utilized with or without the clutch assembly 40 to control rotation of the drive unit 30.

With reference to FIGS. 7A-8B, the planetary gear set crossbow cocking assembly 10 is illustrated coupled with the crossbow frame. In order to better illustrate the cocking assembly, the stock is not shown. The bowstring latch assembly 100a is illustrated in the cocked position, and the bowstring latch assembly retainment lever (retainment device) 200 is engaged with the bowstring latch assembly 100a in position 200a, to retain the bowstring latch assembly 100a in the cocked position. The bowstring latch assembly retainment lever 200 is selectively moved between position 200a retainment position to a release position 200b, allowing the bowstring latch assembly 100a to move.

With reference to FIG. 9C, the planetary gear assembly 20 is operably coupled to a spool winding surface 51. The strap 61 is operably coupled to the spool winding surface 51 and to the bowstring latch assembly 100a. The bowstring latch assembly retainment lever 200 is coupled to the crossbow frame. The bowstring latch assembly 100a engages and retains the bowstring. The crank handle 80 is operably coupled with the drive shaft 24, and as the user rotates the crank handle 80, the drive shaft 24 and sun gear 21 rotate in a first direction, winding the strap 61 under tension onto the spool winding surface 51 and moving said bowstring and bowstring latch assembly 100a to a proximal position as to engage the bowstring latch assembly 100a with the bowstring latch assembly retainment lever 200. The crank handle 80 is rotated a second direction releasing tension of the strap 61, and the bowstring latch assembly retainment lever 200 retains the bowstring and the bowstring latch assembly 100a in the cocked position.

There are three disclosed embodiments of the crank shaft anti-reverse in this parent application. The three embodiments are applied in the continuation-in-part as well. In FIG. 4A, the first embodiment has a gear 99 and a pawl 97 operably coupled to the drive shaft 24. In FIG. 4B, the second embodiment has a one way bearing 44 operably coupled to the drive shaft 24, and the anti-reverse lever 97. The anti-reverse lever 97 and the ratchet gear 99 only allow the drive shaft 24 to rotate in one direction, unless the anti-rotation lever 97 is released from the ratchet gear 99. In FIGS. 1 and 9B, the third embodiment operably couples a clutch assembly 40 with the drive shaft 24. Depending on the embodiment of anti-reverse, and whether or not the crossbow has the bowstring latch assembly retainment lever 200, there are different steps to cocking and de-cocking the crossbow.

To de-cock the crossbow with the first embodiment and no retainment, the crank handle 80 is rotated in the first direction, imparting tension on the strap 61. The user selectively disengaging the pawl 97 from the gear 99 by manipulation of the pawl 97, then rotating the crank handle 80 in the second direction, unwinding the strap 61 from the spool winding surface 51, returning the bowstring latch assembly 100a to the distal position of the crossbow.

Concerning the crossbow of the first embodiment and the bowstring latch assembly retainment lever 200, the crank handle 80 is rotated in the first direction imparting tension on the strap 61. The user selectively disengaging the pawl 97 from the gear 99 by manipulation of the pawl 97, and selectively disengaging the bowstring latch assembly retainment lever 200, then rotating the crank handle 80 in the second direction, unwinding the strap 61 from the spool winding surface 51, and returning the bowstring latch assembly 100a to the distal position of the crossbow.

To de-cock the crossbow in the second embodiment without retainment, the crank handle 80 is rotated in the first direction, imparting tension on the strap 61. The user selectively disengages the one-way bearing 44, then rotates the crank handle 80 in the second direction, unwinding the strap 61 from the spool winding surface 51, and returning the bowstring latch assembly 100a to the distal position of the crossbow.

To de-cock the crossbow in the second embodiment and the bowstring latch assembly retainment lever 200, the crank handle 80 is rotated in the first direction imparting tension on the strap 61. The user selectively disengages the one-way bearing 44, and selectively disengages the bowstring latch assembly retainment lever 200, then rotating the crank handle 80 in the second direction, unwinding the strap 61 from the spool winding surface 51, and returning the bowstring latch assembly 100a to the distal position of the crossbow.

To de-cock the crossbow with the third embodiment and no retainment, the crank handle 80 is rotated in the second direction, unwinding the strap 61 from the spool winding surface 51, and returning the bowstring latch assembly 100a to the distal position of the crossbow. In the third embodiment, the clutch assembly 40 prevents unwanted anti-reverse movement of the clutch assembly 40.

To de-cock the crossbow in the third embodiment with the bowstring latch assembly retainment lever 200, the crank handle 80 is rotated the first direction, imparting tension on the strap 61. The user selectively disengages the bowstring latch assembly retainment lever 200, then rotating the crank handle 80 in the second direction, unwinding the strap 61 from the spool winding surface 51, and returning the bowstring latch assembly 100a to the distal position of the crossbow. In the third embodiment, the clutch assembly 40 prevents unwanted anti-reverse movement of the assembly.

With reference to FIGS. 9A-10B, the planetary gearbox assembly 20 is in vertical alignment with the spool winding surface 51. In the preferred embodiment, the drive shaft 24 has an integrated sun gear 21. Planet gears 22 are radially retained by axles 98 in a fixed carrier 23. The ring gear 28 is coupled with a spool winding surface 51. The ring gear 28 engages, and is driven by the planet gears 22, the ring gear 28 rotates axially about the axis of the sun gear 21. The spool winding surface 51 may be coupled with a spool side 33 and a spool side 35.

The carrier 23 is fixed and radially retained by a carrier boss 23a in the housing cap 10a. The carrier 23 has a carrier bore relative to the axis of the planetary gearbox assembly 20. The drive shaft 24 is on the same axis as the carrier bore.

A flywheel 48 is radially fixed with the inner race of the one-way bearing 44. A compression nut 45 has internal threads sized to engage threads on a first end of the drive shaft 24. As the crank handle 80 is rotated the in first direction, it engages the compression nut 45 with the flywheel 48, compression forces tighten the flywheel 48 with the friction plate 42 and the pressure plate 43. The pressure plate 43 is radially coupled with the sun gear 21, and axial the driveshaft 24. The compression forces rotate the drive shaft 24 and sun gear 21, which in turn rotate the planet gears 22 within the carrier 23, which in turn rotate the ring gear 28 and the spool winding surface 51, winding the strap 61 about the spool winding surface 51.

The planetary gearbox assembly 20 components may be supported within the assembly by bearings, bushings, housings, or cavities. The preferred embodiment uses of bearings for tight tolerances and smooth operation.

With reference to FIGS. 12A-14C, an alternative embodiment of a planetary gearbox assembly 20a provides a more compact mechanism. Fewer components allow for a more economical solution, and expand the versatility of the planetary gearbox assembly 20a. The planetary gearbox assembly 20a is axial to a spool winding surface 51a. A drive shaft 24a includes an integrated sun gear 21 and an integrated flywheel 43a in a solitary component. However, the drive shaft 24a and the flywheel 43a may be fabricated from separate components. A first spool side 33 is rotatably retained on an outer perimeter of a first carrier half 23b. A second spool side 35 is rotatably retained on an outer perimeter of a second carrier half 23b. The first and second carrier halves 23b, 23c do not rotate relative to housing on a crossbow frame. A plurality of gear axles 98 extend outward from an inside surface of the second carrier half 23c. The plurality of gear axles 98 are sized to rotatably receive a plurality of planet gears 22. An internal ring gear 28 is preferably attached to the first and second spool sides 33, 35 with a plurality of fasteners (not shown). A winding surface 51a is formed on an outer surface of the internal ring gear 28. Rotation of the ring gear 28 is driven by the plurality of planet gears 22. The ring gear 28 rotates concentric with an axis of the sun gear 21 through rotation of the plurality of planet gears 22.

The first and second carrier halves 23b and 23c are preferably fixed in a housing, such as item 29 in FIGS. 2A-2C. The first carrier half 23b is attached to the second carrier half 23c with a plurality of threaded fasteners (not shown) inserted through the first carrier half 23b and threaded into the plurality of gear axles 98. A nut bore 81 is formed through the first carrier half 23b to receive a compression nut 45. An axle bore 83 is formed through the second carrier half 23c to receive the drive shaft 24a. The drive shaft 24a is on the same axis as the first and second carriers 23b, 23c.

The compression nut 45 has internal threads sized to engage a threaded end 26 on an end of the drive shaft 24a. With reference to FIG. 1, as the crank handle 80 is rotated in the first direction, compression forces tighten the flywheel 43a with the friction plate 42 and the pressure plate 48a. The pressure plate 48a is radially coupled with the sun gear 21, and axial with the driveshaft 24a. The pressure plate 48a preferably includes a plate portion 55 and a collar portion 57. A drive shaft bore 58 is formed through a length of the pressure plate 48a. A bearing key 63 extends from an outer perimeter of the collar portion 57. The bearing key 63 is sized to be received by a keyway 65 in the one way bearing 44. Thus, the pressure plate 48a is rotationally fixed with the inner race of the one-way bearing 44.

As the crank handle 80 is rotated in a first direction, the compression nut 45 rotates on the threaded end 26 creating compression forces to a thrust bearing 25a, drawing the body of the drive shaft 24a, the pressure plate 48a, the friction disk 42, and the flywheel 43a towards the compression nut 45 (the compression force). The compression force allows for the rotation of the winding surface 51a in the first direction without the unwanted rotation in the second direction. The driveshaft 24a is rotated in the first direction through the handle 80, which in turn rotates the plurality of planet gears 22 within the first and second carrier halves 23b and 23c. The plurality of planet gears 22 rotate the ring gear 28 and the spool winding surface 51a, which causes the strap 61 to wind on the winding surface 51a.

With reference to FIG. 7a, a bowstring drawing assembly 100a is coupled to the planetary gearbox assembly 20a with the strap 61. When engaged with the bowstring, the bowstring drawing assembly 100a selectively retains the bowstring. As the crank handle 80 is rotated in the first direction, the strap 61 is wound on the winding surface 51a which transitions the bowstring from an at-rest position to a cocked position, which creates stored energy in bow limbs (not shown). The stored energy in the bow limbs is a constant force biasing the strap 61 to unwind from the spool winding surface 51a, which maintains the compression forces on the friction plate 42, preventing the unwinding of the strap 61 when the user stops rotating the crank handle 80. At any point between the at-rest position and the cocked position, the user may cease rotation of the crank handle 80 without the strap 61 unwinding from the winding surface 51a.

The user may rotate the crank handle 80 in the second direction allowing controlled unwinding of the strap 61 from the winding surface 51a. This is accomplished due to the compression forces of the planetary gearbox assembly 20a, in that as the crank handle 80 is rotated in the second direction to loosen the compression nut 45 on the threaded end 26 and just momentarily overcoming the stored energy of the bow limbs and constant biasing forces on the strap 61. Again, the user may cease rotation of the crank handle 80 at any point wherein the compression forces seize the rotation of the winding surface 51a.

The planetary gearbox assembly 20a components may be supported within the assembly by bearings, bushings (for alignment), housings, or cavities. The preferred embodiment uses bearings for tight tolerances and smooth operation.

The preferred embodiment is described and illustrated within; however, the invention is not limited to the preferred embodiment.

While particular embodiments of the invention have been shown and described, it will be obvious to those skilled in the art that changes and modifications may be made without departing from the invention in its broader aspects, and therefore, the aim in the appended claims is to cover all such changes and modifications as fall within the true spirit and scope of the invention.

Claims

1. A cranking mechanism for a crossbow comprising: a drive shaft includes a sun gear;a carrier rotatably retains a plurality of planet gears, said sun gear drives said plurality of planet gears;an internal ring gear includes a spool winding surface formed on an outer perimeter, said plurality of planet gears drive said internal ring gear, wherein one end of a strap is retained on said spool winding surface;a first spool side and a second spool side, said internal ring gear is retained between said first and second spool sides, said carrier is rotatably retained in said first and second spool sides; anda one-way rotation device is retained on said drive shaft, wherein said one-way rotation device only allows said drive shaft to be rotated in one direction unless said one-way rotation device is operably released.

2. The cranking mechanism for a crossbow of claim 1, further comprising: a bowstring drawing device is connected to an opposing end of the strap, the bowstring drawing device is one of a sled, a hook, or a bowstring latch assembly.

3. The cranking mechanism for a crossbow of claim 1, further comprising: said drive shaft is terminated with a threaded end;a compression nut is threaded on to said threaded end; anda handle includes a cavity to receive said compression nut.

4. The cranking mechanism for a crossbow of claim 2, further comprising: said bowstring latch assembly is coupled to the crossbow frame, said retainment device selectively retains said bowstring latch assembly in a cocked position, or selectively releases said bowstring latch assembly from the cocked position.

5. The cranking mechanism for a crossbow of claim 3, further comprising: said handle is retained on a driven end of said drive shaft.

6. A cranking mechanism for a crossbow comprising: a planetary gear set includes a drive sun gear, a plurality of planet gears in a radially fixed carrier, and a driven ring gear, said ring gear includes a spool winding surface on an outer perimeter thereof;a drive shaft includes a first driven end and a second axially retained end, said sun gear is integrated into said drive shaft;said carrier includes a plurality of axles to rotatably retain said plurality of planet gears, said sun gear causes rotation of said plurality of planet gears within said carrier, said plurality of planet gears engage said ring gear, wherein rotation of said plurality of planet gears causes rotation of said ring gear and said spool winding surface in a direction opposite of said drive shaft;a strap includes a spool end, said spool end is fixed to a winding diameter of said spool, wherein rotation of said drive shaft winds said strap on said winding diameter;a clutch is retained on said drive shaft;a one-way bearing rotation device is engaged with said clutch, axial tension is applied to said one-way bearing and said clutch in a first direction through said driven end to wind said strap on said spool winding surface; andwherein said cranking mechanism for a crossbow is one of built-in to said crossbow and removable from said crossbow.

7. The cranking mechanism for a crossbow of claim 1, further comprising: a bowstring drawing device is connected to said strap at an end said spool end, said bowstring drawing device is one of a sled, a hook, and a bowstring latch assembly.

8. The cranking mechanism for a crossbow of claim 6, further comprising: a bowstring latch assembly retainment device coupled to the crossbow frame, said retainment device selectively retains said bowstring latch assembly in a cocked position, or selectively releases said bowstring latch assembly from the cocked position.

9. The cranking mechanism for a crossbow of claim 6, further comprising: a tension nut is threaded on to said first driven end of said drive shaft; anda handle includes a cavity to receive said tension nut.

10. The cranking mechanism for a crossbow of claim 6 wherein: said clutch includes a pressure plate and a friction plate, said pressure plate is engaged with said one-way bearing, said friction plate makes contact with said pressure plate and said spool.

11. The cranking mechanism for a crossbow of claim 6 wherein: said driven end is rotated in a second direction to disengage said clutch to allow said strap to be unwound from said spool;wherein ceasing rotation in said second direction re-engages said clutch and prevents unwinding of said strap.

12. The cranking mechanism for a crossbow of claim 6 wherein: said driven end is rotated in a second direction to disengage said clutch to allow said strap to be unwound from said spool, wherein ceasing rotation in said second direction re-engages said clutch and prevents unwinding of said strap; and wherein rotation in the first direction to re-engage clutch allowing said strap to wind on the winding surface.

13. The method of operating a crossbow and a planetary gear set crossbow cocking device, wherein: coupling operably providing a planetary gear set and drive shaft to a spool winding surface, one end of a strap is operably coupled to said spool winding surface, a bowstring latch assembly is retained on an opposing end of the strap;coupling a bowstring latch assembly retainment device to the crossbow frame, the bowstring latch assembly engages and retains the bowstring;coupling operably a crank handle with the drive shaft, the crank handle rotates the drive shaft and the sun gear in a first direction winding the strap under tension onto the spool winding surface and moving the bowstring and bowstring latch assembly to a proximal position as to engage said bowstring latch assembly with said bowstring latch assembly retainment means;said crank handle is rotated a second direction releasing tension of the strap, said bowstring latch assembly retainment device retains the bowstring and the bowstring latch assembly in a cocked position;de-cocking the crossbow with the crank handle by rotating the crank handle in is rotated the first direction to impart tension on the strap, the user selectively disengaging the bowstring latch assembly retainment device from the bowstring latch assembly, then rotating the crank handle in the second direction to unwind the strap from the spool winding surface, returning the bowstring latch assembly to the distal position of the crossbow.

14. The method of operating a crossbow and a planetary gear set crossbow cocking device of claim 13 wherein; the crossbow cocking device includes a ratchet gear and a pawl operably coupled with the planetary gear set.

15. The method of operating a crossbow and a planetary gear set crossbow cocking device of claim 13 wherein; the crossbow cocking device includes a one-way bearing, a ratchet gear and a pawl operably coupled with the planetary gear set.

16. The method of operating a crossbow and a planetary gear set crossbow cocking device of claim 13 wherein; the crossbow cocking device includes a one-way bearing and clutch assembly operably coupled with the planetary gear set.

17. The method of operating a crossbow and a planetary gear set crossbow cocking device wherein; coupling operably a planetary gear set and drive shaft to a spool winding surface;coupling operably a drive shaft to said spool winding surface and to a bowstring latch assembly, a sun gear is retained on said drive shaft;engaging the bowstring latch assembly with the bowstring, retaining the bowstring in the bowstring latch assembly;coupling operably a handle with the drive shaft;rotating the drive shaft and the sun gear with the crank handle in a first direction, winding the strap under tension onto the spool winding surface, moving the bowstring and bowstring latch assembly to a cocked position; androtating the crank handle in the second direction to uwind the strap from the spool winding surface, returning the bowstring latch assembly to a distal position of the crossbow.

18. The method of operating a crossbow and a planetary gear set crossbow cocking device of claim 17 wherein; the crossbow cocking device includes a ratchet gear and a pawl operably coupled with the planetary gear set.

19. The method of operating a crossbow and a planetary gear set crossbow cocking device of claim 17 wherein; the crossbow cocking device includes a one-way bearing, a ratchet gear and a pawl operably coupled with the planetary gear set.

20. The method of operating a crossbow and a planetary gear set crossbow cocking device of claim 17 wherein; the crossbow cocking device includes a one-way bearing and a clutch assembly operably coupled with the planetary gear set.