Gas-powered semi-automatic air rifle bolt

Abstract

The air gun is equipped with a semi-automatic bolt action.

Description

[0001] Cross-reference to related applications

[0002] This international application claims the benefit and priority of U.S. Patent Application No. 17 / 152,550, filed January 19, 2021, the entire disclosure of which is incorporated herein by reference.

[0003] Statements related to federally sponsored research and development

[0004] not applicable

[0005] References to sequence lists, tables, or computer program listings in CD appendices

[0006] not applicable Technical Field

[0007] This invention relates to an air gun having a bolt capable of semi-automatic firing. Background Technology

[0008] As is well known, air guns can provide semi-automatic action. In some cases, a revolver-style bolt is used, where the force of pulling the trigger advances one of a plurality of pre-loaded bullets to the firing position and cocks the hammer to fire. An example of this is U.S. Patent No. 5,285,766, filed by Milliman on July 30, 1992, entitled "Gun with Removable Rotary Ammunition Clip".

[0009] Other air guns ensure semi-automatic operation by transferring propellant, such as pressurized gas from a supply device, to propel the ammunition, thereby operating the bolt.

[0010] Some air guns attempt to recycle used pressurized propellant gas for operating the bolt. This approach increases the weight, cost, and complexity of the air gun. An example of this can be found in document EP 1729082, titled "Automatic Gas Powered Gun," submitted by Axelsson around June 3, 2005.

[0011] Some air guns also use electronic and electromechanical systems to provide semi-automatic operation. The use of electronic and electromechanical systems increases weight, cost, and complexity. An example of such an air gun is described in U.S. Patent No. 8,578,922, filed by Granger on July 17, 2009.

[0012] What is needed in this field is an air gun and a method for operating an air gun, enabling the operation of the air gun in an efficient, lightweight and cost-effective manner. Summary of the Invention

[0013] An air gun and a method of operating the air gun are provided. In one aspect, the air gun includes: a valve configured to release pressurized gas when the valve stem moves from a closed position and a series of open positions; a hammer, biased by a hammer spring and moved from a lever position along a hammer path to drive the valve from a closed position through the series of open positions, causing the valve to release a flow of pressurized gas; and a primary sear movable between a primary sear lever position and a primary sear return position, wherein in the primary sear lever position, the primary sear hammer engagement portion is located in the hammer path to hold the hammer in the lever position, and in the primary sear return position, the primary sear return surface is located in the hammer path. The secondary sear is movable between the secondary sear-raised position and the secondary sear-fire position. In the secondary sear-raised position, it prevents the primary sear from moving from the primary sear-raised position to the primary sear-fire position. In the secondary sear-fire position, it allows the primary sear to move from the raised position to the fire position, allowing the hammer to strike the valve stem. A secondary sear spring biases the secondary sear toward the secondary sear-raised position. The trigger is movable between the non-fire trigger position and the fire trigger position, and a lifting element movable between the engaged positions connects the secondary sear to the trigger, so that as the trigger moves to the fire trigger position, the secondary sear moves to the fire trigger position, allowing the hammer to move the primary sear from the primary sear-raised position to the primary sear-return position. During firing, a portion of the gas released from the valve travels into the hammer path and drives the hammer along the hammer path away from the valve stem, causing the hammer to travel to the return position and drive the primary sear from the return position to the primary sear-raised position; and after firing, the lifting element disengages to allow the trigger and secondary sear to move separately / individually, causing the secondary sear to move to the secondary sear-raised position, thereby holding the primary sear in the primary sear-raised position before the hammer spring biases the hammer to move it from the return position to the raise position. Attached Figure Description

[0014] Figure 1 This is a cross-sectional view of one embodiment of a pre-charged gas air gun, with portions of the stock and barrel removed.

[0015] Figure 2 yes Figure 1 A partial cross-sectional right-side view of the embodiment is shown to illustrate the flow of pressurized airflow when the valve is opened.

[0016] Figure 3 yes Figure 1 A partial cross-sectional right-side view of the embodiment is shown to illustrate the release of pressurized gas from the hammer path.

[0017] Figure 4 yes Figure 1 A partial cross-sectional view of the right side of the embodiment, showing the valve open.

[0018] Figure 5 yes Figure 1 A partial cross-sectional view of the right side of an air gun, showing a first embodiment of the air gun with a bolt in the cocked position and the safety device disengaged.

[0019] Figure 6 yes Figure 5 Enlarged view of the right side of a partial cross-section of the bolt of an air gun, showing the first embodiment of the bolt, with the bolt in the cocked position and the safety device disengaged.

[0020] Figure 7 yes Figure 5 The right-side partial cross-sectional view of the bolt shows the trigger in the raised position with the safety disengaged, the trigger in the firing position, and the hammer advancing to a position where the spring force and the raising force are approximately equal, ending the hammer's movement in the firing direction.

[0021] Figure 8 It is the hammer system and Figure 5 The right-side partial cross-sectional view of the bolt carrier shows the hammer moving in the lifting direction until it makes contact with the deflecting surface of the primary sear.

[0022] Figure 9 It is the hammer system and Figure 5 The right side of the partial cross-section of the bolt is enlarged. At this point, the hammer is moving towards the return position. In the return position, the spring force and the lifting force are roughly equal, ending the hammer's movement in the lifting direction.

[0023] Figure 10 It is the hammer system and Figure 5 The right side of the partial cross-section of the bolt carrier shows the hammer moving from the return position toward the firing position.

[0024] Figure 11 A top view shows one embodiment of a secondary sear and a portion of a safety device.

[0025] Figure 12 yes Figure 1 A partial cross-sectional view of the right side of an air gun, showing a first embodiment of the air gun with a bolt in the cocked position and the safety device engaged.

[0026] Figure 13 yes Figure 13 The front, right, and top perspective cross-sectional views of the bolt carrier implementation, in which a portion of the secondary sear is cut off.

[0027] Figure 14 It is the hammer system and Figure 6 The right side of the partial cross-section of the bolt is enlarged, showing the hammer moving toward the hammer return position and engaging the primary sear.

[0028] Figure 15This is a right-side cross-sectional view of one implementation of the reloading system, where the trigger has just been pulled to the firing position and the bolt is in the firing position.

[0029] Figure 16 yes Figure 15 The enlarged view of the indicated part.

[0030] Figure 17 yes Figure 15 The right-side partial cross-sectional view of the embodiment shows the bolt in the returned position.

[0031] Figure 18 yes Figure 1 A partial cross-sectional right-side view of the embodiment, wherein the bolt is positioned to engage with the projectile during loading. Detailed Implementation

[0032] Figure 1 This is a cross-sectional view of one embodiment of a pre-charged gas air gun 10, with portions of the stock 12 and barrel 14 cut off. Figure 2 yes Figure 1 A partial cross-sectional view of the embodiment is shown to illustrate the flow of pressurized gas when the valve is opened. Figure 3 yes Figure 1 A partial cross-sectional right-side view of the embodiment to show the release of pressurized gas from the hammer path. Figure 4 yes Figure 1 The implementation method is shown in a partial cross-sectional view on the right side when the valve is open.

[0033] like Figure 1 As shown, the air gun 10 has a stock 12, a barrel 14 with a chamber 16, a projectile loading system 18, and a projectile storage system 20. The projectile storage system 20 is capable of storing multiple individual projectiles 26 and can cooperate with the projectile loading system 18 to position one of the projectiles 26 in the loading area 21.

[0034] The projectile loading system 18 and the projectile storage system 20 are designed such that during the loading process, one of the plurality of projectiles 26 stored in the projectile storage system 20 can be moved to the loading area 21, and the projectile 26 from the loading area can be finally propelled through the barrel 16.

[0035] In the illustrated embodiment, the projectile storage system 20 is a removable projectile storage system 20, and is configured to cooperate with the projectile loading system 18 to removably position the storage system 20 such that the loading area 21 is positioned where movement of the bolt 24 can drive the projectile 26 into the chamber 16. Other embodiments are also possible.

[0036] The use of a removable projectile storage system 20 to store projectiles 26 is merely exemplary, and in other embodiments, other forms of projectile storage systems 20 may be used, including but not limited to belts, chains, turntables, drums, or any other form of projectile storage system 20. In various embodiments, the projectile storage system 20 may be separable from the air gun 10 as described in this embodiment, or it may be integrated with the air gun.

[0037] A supply device for pressurized gas 30 includes a pressurized gas container 32, which supplies pressurized gas for operating the air gun 10.

[0038] exist Figure 1 In one embodiment, an optional regulator 34 is provided, which is adapted to receive gas from a pressurized gas container 32, the received gas having a first pressure range, and the regulator provides a regulating gas having a second pressure range, which is smaller than the first pressure range, to ensure more consistent operation of the air gun.

[0039] In this embodiment, the regulating and pressurizing gas storage chamber 36 is connected between the regulator 34 and the valve 40, and provides the valve 40 with a buffer volume of regulating and pressurizing gas.

[0040] Valve 40 is configured to release pressurized gas from the supply device of pressurized gas 30 or from the regulating, pressurized gas storage chamber 36 when valve stem 46 moves against bias pressure relative to other parts of valve 40.

[0041] In this embodiment, valve 40 has a valve body 41, an input portion 42 of which is connected to a pressurized gas storage chamber 36, a valve seat 43, a valve stem path 44, a valve seal 45, and a valve output path 48.

[0042] Valve seal 45 is mechanically connected to valve stem 46 and is movably positioned within valve body 41 between a sealed position and one of a series of non-sealed positions, such as... Figure 1 As shown, in the sealed position, the valve seal 45 is closed against the valve seat 43, while in a series of unsealed positions, the valve body 41 is separated from the valve seat 43 to allow pressurized gas to flow through the valve seat 43 and the valve seal 45. Figure 2 An example of this unsealed position is shown in the figure.

[0043] In this embodiment, the valve stem 46 is slidably located in the valve stem path 44, and the cross-sectional diameter of the valve stem path 44 is at least a certain amount larger than the diameter of the valve stem 46, such an amount being sufficient to allow this movement. Furthermore, as will be described in more detail below, the diameter (DVST) of the valve stem path 44 relative to the diameter (DVS) of the valve stem 46 can be excessively large by a certain amount, such an amount being sufficient to allow the airflow described later herein.

[0044] The valve seal 45 is biased against the valve seat 43 by a combination of the valve sealing force VCF provided by the pressurized gas from the chamber 36 and the valve sealing spring 49.

[0045] exist Figure 1 and Figure 2 In the illustrated embodiment, the valve seal 45 and the valve stem 46 are mechanically connected such that movement of the valve stem 46 within the valve stem path 44 requires associated movement of the valve seal 45. In this embodiment, the valve seal 45 and the valve stem 46 are directly connected. The valve stem 46 is aligned with the axis of motion of the valve seal 45, which lies between a closed position where the valve seal 45 abuts against the valve seat 43 and a series of positions where the valve seal 45 is separated from the valve seat 43. The hammer system 60 has a hammer 64, which is movable along the hammer path 68 at least between a raised position and a series of firing positions. A hammer spring 62 pushes the hammer 64 from the raised position through the series of firing positions.

[0046] In the illustrated embodiment, valve 40 provides a hammer path end wall 66 that terminates in a hammer path 68 via a valve stem path 44. This valve stem path provides a path from the hammer path end wall 66 to the valve seal 45, allowing the valve stem 46 to extend from the valve seal 45 into the hammer path 68. In other embodiments, the hammer path end wall 66 may be part of a structure other than valve 40.

[0047] like Figure 1 As shown, valve 40 is configured and positioned such that valve stem 46 extends from hammer path end wall 66 in hammer path 68 beyond the closing valve extension distance VED when valve 40 is closed. Furthermore, valve 40 is configured such that valve stem 40 can be moved by hammer 64 to release pressurized gas through valve 40 in a series of open positions, including... Figure 2 The return position shown is separated from the hammer path end wall 66 by a valve return extension distance CVED smaller than the valve closing extension distance CVED.

[0048] The bolt 70 has a firing control system 76 that holds the hammer 64 in the cocked position until the user fires the air gun 10 by operating the safety device 80 and the trigger 100. Figure 1 As can be seen, when the bolt 70 holds the hammer in the raised position, the hammer 64 and the valve stem 46 remain separated by the hammer acceleration distance HAD.

[0049] When the bolt 70 releases the hammer 64, the hammer spring 62 accelerates the hammer 64 by a hammer acceleration distance HAD, so as to use the hammer force HF to strike the valve seat 46. The hammer force is sufficient to move the valve stem 46 and the valve seal 45 from the closed position to the series of open positions through which the valve seal 45 is separated from the valve seat 43.

[0050] like Figure 2 As shown, in this embodiment, a stream of regulated pressurized gas 51 flows around the valve seal 45 to provide a release flow 53 of the regulated pressurized gas. A portion of the release flow 53 generates a kinetic flow 55 that flows through the valve output path 48 to the transmission pipe 58, and another portion of the release flow 53 generates a flapping flow 57 that flows between the valve stem path 44 and the valve stem 46.

[0051] exist Figure 1 and Figure 2 In the illustrated embodiment, the power flow 55 is guided by the transmission tube 58 to the accumulation cavity 56 between the bolt 24 and the projectile 26. An optional bolt seal 28, such as an O-ring, provides a seal between the bolt 24 and the chamber 16 on one side of the transmission tube 58, while the projectile 26 provides resistance to gas flow on the other side of the transmission tube 58.

[0052] Because the chamber 16 is configured to expand only within a very limited range when exposed to the power flow 55, pressurized gas from the power flow 55 begins to accumulate in an accumulation cavity 56, at least between the bolt 24 and the projectile 26, and optionally also between the chamber 16 and the bolt seal 28. The bolt 24, the projectile 26, and any other structures forming the accumulation cavity 56 are exposed to the forces generated when the power flow 55 enters the accumulation cavity. As the power flow 55 enters the accumulation cavity 56, both pressure and resistance increase, eventually rising to a level that transmits the force required to eject the projectile 26 from the chamber 16 within a predetermined range.

[0053] In this embodiment, the accumulator cavity 56 is partially provided by a channel 241 in the bolt 24, the channel being shaped to receive the power flow 55 and expose the projectile 26 to the pressure generated when the power flow 55 flows into the accumulator cavity 55.

[0054] In other embodiments, the projectile 26 may be shaped to provide an accumulation cavity 56 along its length and to provide a path for the power flow 55 to flow into the length of the projectile 26. In other embodiments, the air gun 10 may be configured such that the bolt 24 or the projectile 26 is separated to provide the accumulation cavity 56, which the power flow 55 can rapidly fill.

[0055] The air gun 10 is configured to keep the projectile 26 substantially stationary until the power flow 55 applies a preset level of power to the projectile 26.

[0056] In a non-limiting example implementation, the size and configuration of the chamber 16 and the projectile 26 are such that the static friction between the chamber 16 and the projectile 26 will provide a holding force that must be overcome before the projectile 26 can pass through the chamber 26.

[0057] Furthermore, in this embodiment, the bore 16 is optionally rifling, such that the projectile 26 must undergo plastic deformation in the form of rifling grooves before traveling along the bore 16. In this regard, the projectile 26 can be made of a material with sufficient ductility to allow such grooves to be formed when a predetermined amount of force is applied to the projectile 26. In such an embodiment, the retaining force can be partially provided by a certain amount of force required to make the projectile 26 conform to the rifling grooves.

[0058] Different configurations of projectile size, barrel size, rifling, and other configurations and mechanisms known in the art can be used to help ensure that the projectile 26 remains relatively stationary until a pressure within a predetermined range is reached in the accumulation cavity 56, and any configuration can be applied here for this purpose.

[0059] Finally, the pressure reaches the preset range, and the projectile 26 is pushed through the chamber 16 to complete the firing cycle.

[0060] In order for the semi-automatic air gun 10 to subsequently return to the cocked and loaded state where valve 40 is closed, hammer 64 is returned to the cocked position, and bolt 70 is reset to hold hammer 64 in the cocked position. The projectile loading system 18 and the projectile storage system 20 pre-place another projectile 26 in the chamber 16 for firing.

[0061] In the embodiments described herein, the air gun 10 returns to the cocking and loading state without the necessary assistance of electronic timing control and actuator, electromechanical timing control and actuator, or manual user intervention, as will now be described.

[0062] Hammer return

[0063] exist Figure 1 and Figure 2 In the embodiment shown, the hammer 64 is returned to the raised position by a combination of a first hammer raising force HCF1 provided to the hammer 64 by the raising flow 57 of pressurized gas and a second hammer raising force HCF2 provided to the hammer 64 by the valve 40.

[0064] from Figures 1-5 As can be seen, the valve stem path 44 is in fluid communication with the valve output path 48, so that the release flow 53 faces two possible flow paths to generate two separate flow streams: the power flow 55 traveling through the valve output path 48 as described above and the lever flow 57 traveling between the valve stem path 44 and the valve stem 46.

[0065] In this type of conventional valve design, to limit losses, gas flow between the stem path 44 and the stem 46 is designed to be restricted or blocked. This can be achieved, for example, by providing a stem path 44 whose first diameter is only slightly larger than the diameter of the stem 46, thus restricting gas travel through the stem tube. In some cases, lubricant between the stem 46 and the stem path 44 provides a sealing effect.

[0066] Conversely, in this embodiment, the shape and size of the valve stem path 44 and the valve stem 46 allow for sufficient flow of the airflow 57 to achieve the purpose described below.

[0067] In this embodiment, the hammer 64, the hammer path 68, and the hammer path end wall 66 are configured to limit the extent to which the lifting flow 57 can escape from the closed area 65, so that the lifting flow 57 enters the closed area 65 to generate lifting pressure, which resists the first hammer lifting force HCF1 generated by the hammer 64.

[0068] like Figure 2 and Figure 4 As shown in the enlarged view, the valve spring 49 is compressed when the valve seal 45 is moved to a series of non-sealing positions. The valve spring 49 resists this compression by applying a second hammer lifting force HCF2.

[0069] As the hammer 64 continues to move in the firing direction, the volume of the enclosed zone 65 decreases, while the levering flow 57 of compressed air continues to be injected into the shrinking enclosed zone 65. As a result, levering pressure is rapidly built up in the enclosed zone 65, causing the amount of the first hammer levering force HCF1 to increase rapidly.

[0070] Furthermore, as the hammer 64 continues to move in the firing direction, the valve seal 45 and valve stem 46 continue to displace relative to the valve body 41, causing the valve spring 49 to elastically deform. This, in turn, stores more and more potential energy in the valve spring 49 and increases its resistance to further elastic deformation. As a result, the second hammer lifting force HCF2 increases, while the kinetic energy from the hammer 64 decreases.

[0071] Finally, hammer 64 drives valve stem 46 to the return position. In the return position, the sum of the first hammer lifting force HCF1 and the second hammer lifting force HCF2 equals the hammering force HF applied by hammer 64 to valve stem 46. Thereafter, hammer 64 begins to accelerate along hammer path 68 in a lifting direction away from valve 40 under the action of the first hammer lifting force HCF1 and the second hammer lifting force HCF2.

[0072] To provide the energy to propel the projectile 26 at high speed into its range, the regulating flow 51 can be maintained at high pressure, which can be, for example, but not limited to, 40-200 times the atmospheric level. Under such pressure, it may only require a momentary opening of the valve 40 to transmit the release flow 53, which generates a power flow 55 that can provide the required thrust to the projectile 26.

[0073] In this implementation, the high pressure of the release flow 53 will allow the lever flow 57 to flow rapidly in the space between the valve stem path 44 and the valve stem 46. The lever flow 57 flows into the enclosed region 65 between the hammer 64, the hammer path end wall 66, and a portion of the hammer path 68 near the valve 40.

[0074] Furthermore, to limit the loss of high-pressure compressed gas, valve 40 can be configured such that one or more forces biasing valve 40 into a closed state can rapidly close valve 40. In such an embodiment, valve spring 49 can have a high spring constant, such that a large force is required to push valve seal 45 away from valve seat 43, and valve spring 49 can quickly return valve seal 45 to abut against valve seat 43 when the force acting on valve stem 46 decreases. Additionally, the gas pressure provided by the pressurized gas contained in valve 40 by valve seal 45 can also increase the force required to open valve 40 and provide a force that facilitates rapid closure of valve 40.

[0075] Given this valve design consideration, the hammer 64 and the hammer spring 62 can be configured to accelerate the hammer 64 so that the hammer 64 strikes the valve stem 46 with sufficient kinetic energy, thereby driving the valve 40 to open.

[0076] As the hammer spring 62 and hammer 64 rapidly dissipate this kinetic energy, hammer 64 drives valve stem 46 from the closed position to the open valve return position, wherein valve stem 46 extends into the closed zone 65 by the open valve return distance OVRD.

[0077] As this kinetic energy is dissipated, the force exerted by the hammer 64 on the valve stem 46 decreases to a level at which the hammer 64 can no longer overcome the force pushing the valve seal 45 and valve stem 46 to close. This occurs when the valve 40 is in the open valve return position. Thereafter, these forces forcefully push the valve seal 45 to the closed valve position against the valve seat 43 and push the valve stem 46 to drive the hammer 64 away from the end wall 67.

[0078] However, it can be seen that when hammer 64 is at the return point, hammer 64 continues to be pushed by hammer spring 62 to maintain contact with valve stem 46. Therefore, in order to close valve 40, sufficient force must be applied to hammer 64 so that hammer 64 moves at least a valve extension distance VED of valve stem 46.

[0079] However, this only allows valve 40 to close. In order to achieve a semi-automatic bolt action, hammer 64 must travel over the length of hammer acceleration distance HAD after contact with valve stem 46 has ended, resisting the push of hammer spring 62.

[0080] Accordingly, in Figure 1 In one embodiment, the air gun 10 is configured to accelerate the hammer 64 by a combination of a first hammer-lifting force HCF1 and a second hammer-lifting force HCF2, so that the hammer 64 will have sufficient kinetic energy to travel at least to the lift position after contact with the valve stem 46, resisting the action of the hammer spring 62.

[0081] In air guns, limiting any unnecessary expenditure of compressed gas can be important. Therefore, Figure 1 The implementation includes a valve 40, which is equipped with a valve spring 49. The valve spring has a certain stiffness to help receive kinetic energy from the hammer 64 and return a certain proportion of the kinetic energy transmitted by the hammer 64 to the valve stem 46 to the hammer 64 through the second hammer lifting force HCF2.

[0082] Because friction and other considerations dictate that this system cannot return all the kinetic energy provided by the hammer 64 to the valve stem 40, the first hammer lifting force HCF1 uses energy from the lifting flow 57. Its primary purpose is to replace the energy lost during firing and to further provide sufficient kinetic energy to compensate for the kinetic energy lost by friction or other forces when the hammer 64 is at least pushed to the lifting position.

[0083] In various embodiments, as time progresses, the application of the first hammer-lifting force HCF1 and the second hammer-lifting force HCF2 is established to give the hammer 64 a preset lifting kinetic energy, which is also at least sufficient to cause the hammer 64 to interact with the bolt 70, causing the bolt 70 to return to the state in which the bolt 70 holds the hammer 64 in the lifted position.

[0084] In various embodiments, a first hammer-lifting force HCF1 and a second hammer-lifting force HCF2 can be established to give the hammer 64 a preset lifting kinetic energy, which is at least sufficient to drive the hammer 64 through the lifted position along the hammer path 68. The bolt 70 is configured to interact with the hammer 64 and return to a state in which the bolt 70 can hold the hammer 64 in the lifted position before the hammer spring 62 pushes the hammer back to the lifted position.

[0085] In this way, the supply of pressurized gas 30 is used to transmit the first hammer lifting force HCF1 and the second hammer lifting force HCF2. The first hammer lifting force supplements the force recovered by the valve spring 49, and the second hammer lifting force is required so that the hammer 64 returns to the lifting position at least. This limits the extent to which such pressurized gas is consumed.

[0086] exist Figure 1 and Figure 2 The illustrated embodiment provides an O-ring 59 to help prevent loss of pressurized air between the hammer path end wall 66 and the hammer path 68.

[0087] Gas management in hammer path

[0088] Understandably, in order for the first hammer lifting force HCF1 to make a predetermined contribution to the kinetic energy required for the hammer 64 to return to the lifting position, the ability of gas to escape from the closed zone 65 must be limited.

[0089] However, it is also understandable that the hammer path 68 typically contains a column of air before the air gun 10 fires. If this column of air becomes trapped in the enclosed zone 65, it is possible that some of the energy from the moving hammer 64 will be consumed when compressing the gas in the hammer path 68. Therefore, it is necessary to manage the gas flow within the hammer path 68 to ensure proper interaction between the hammer 64 and the valve 40.

[0090] like Figure 3 As best described in this embodiment, the hammer path 68 includes a gas outlet 69. The gas outlet 69 is separated from the hammer path end wall 66 by a closed distance CD.

[0091] As the hammer 64 travels toward the valve stem 46 during firing, air in the hammer path 68 is pushed out of the hammer path 68 through the gas outlet 69. However, as the hammer 64 moves within a series of positions separated from the hammer path end wall 66 by a distance greater than the closing distance CD, the gas located between the hammer 64, the hammer path end wall 66, and the hammer path 68 can freely transfer out of the hammer path 68 through the gas outlet 69.

[0092] Therefore, as the hammer 64 travels to the impact valve stem 46, the gas outlet 69 limits the amount of gas available for pressurization between the hammer 64, the hammer path end wall 66, and the hammer path 68, and primarily provides management of the gas in the hammer path 68 during firing.

[0093] Alternatively, a further mechanism for managing the gas in the hammer path 68 is the availability of space between the stem path 44 and the stem 46 to receive air from the hammer path 68. That is, as described above, the stem path 44 provides an opening in the end wall 66 of the hammer path into which air can flow after the hammer 64 passes through the gas outlet 69. However, as discussed above, the presence of the stem 46 in the stem path 44 restricts the flow of any one or more gases through the stem path 44.

[0094] The opening sequence or relative timing of valve 40 can be adjusted, as well as the interference of hammer 64 on the gas flow from gas outlet 69, to manage the pressure generated by the gas in hammer path 68 as needed.

[0095] For example, in various embodiments, such as in Figure 1 In the embodiment shown, the valve stem 46 has a closing valve extension distance CVED that is larger than the closing distance CD, such that the hammer 64 strikes the valve stem 46 where the hammer 64 does not completely block the flow of gas through the gas outlet 69.

[0096] This is Figure 3 As illustrated in the figure, this diagram shows the situation at the point in time when the hammer 64 is close to but has not yet made contact with the valve stem 46. This prevents the formation of the closed zone 65 only after the hammer 64 strikes the valve stem 46, and thus limits any kinetic energy loss in the hammer 64 that may be caused by gas compression in the hammer path 68.

[0097] However, as Figure 4 As shown, the impact force between the hammer 64 and the valve stem 46 drives the valve stem 46 through a series of open positions, including a position where the hammer 64 restricts gas flow through the gas outlet 69 to form a closed zone 65. As described above, the compression effect of the movement of the hammer 64 on any remaining gas in the closed zone 65 may be limited by the ability to compress the gas flow through the hammer tube along the valve stem path 44.

[0098] In various embodiments, when the hammer 64 drives the valve stem 40 to the return position, the volume of the closed area 65 may decrease. In the return position, the valve stem 46 extends from the hammer path end wall 66 into the hammer path 68 by an open valve return distance OVRD.

[0099] When this occurs, the lifting flow 57 flows into the closed region 65. The reduction in volume of the closed region 65 and the injection of the lifting flow 57 into the closed region 65 combine to generate lifting pressure, which acts on all surfaces forming the closed region 65.

[0100] Understandably, while this approach can manage the risk of energy loss related to compression during launch, it limits the extent to which the second hammer-lifting force HCF2 can act on hammer 64 to impart kinetic energy during lifting.

[0101] Specifically, it can be understood that when hammer 64 is moved in the lifting direction, hammer 64 passes through gas outlet 69. This allows the lifting flow 57 to escape through gas outlet 69 and terminates the contribution of the first hammer lifting force HCF1 to the accelerating hammer 64 in the lifting direction.

[0102] Since the gas outlet 69 is separate from the lifting position, the hammer lifting flow 57 must ensure that the first hammer lifting force HCF1 has provided any required kinetic energy to the hammer 64 before the hammer 64 passes through the gas outlet 69.

[0103] Therefore, the diameter of the valve stem path 44 will be larger than the diameter of the valve stem 46 to the extent that a certain volume of the flap flow 57 enters the closed region 65.

[0104] Similarly, the characteristics of the stem path 44, the stem 46, and the elements forming part of the closed area 65 will be adapted to ensure that the hammer 64 receives any necessary kinetic energy within the available time.

[0105] In various embodiments, the amount by which the cross-sectional area of ​​the valve stem path 44 is excessive relative to the cross-sectional area of ​​the valve stem 46 is calculated to allow the release flow 53 to generate a lever flow 57, which flows through the valve stem path 44 at a preset speed and enters the hammer path 68. This preset speed is determined at least in part based on the available gas pressure, the cross-sectional area of ​​the lever pressure that can act on the hammer 64, the pressure of the release flow 53, the pressure of the lever flow 57, and so on.

[0106] Similarly, the spring stiffness of valve spring 49, the closing valve extension distance VED, and the return extension distance RED can be determined to optimize the kinetic energy of hammer 64 through valve stem 46 to the return of hammer 64 during the time it takes for hammer 64 to be pushed from the opening valve extension distance OVED to the closing valve extension distance CVED.

[0107] In various embodiments, the hammer path endwall 66 may be provided with an opening (not shown) shaped to receive the lever flow 57 from the valve stem path 44 and to control the range, rate, or distribution of the lever flow 57 as it flows into the hammer path 68.

[0108] exist Figure 1 In this embodiment, the hammer system 60 is shown with an optional degassing system 50. The degassing system 50 allows the user to manually drive the hammer 64 into controlled, continuous contact with the valve stem 46 using a special tool, thereby allowing controlled release of gas from the supply of pressurized gas 30, for example, when the user wishes to release stored gas pressure when the air gun is not in use.

[0109] Therefore, various embodiments of the air gun 10 are provided with a valve 40 and a hammer system 60, in which the hammer 64 is pushed to move rapidly from a cocked position away from the valve 40 to a position in contact with the valve, causing the valve 40 to open. Sufficient kinetic energy is then imparted to the hammer 64 using a combination of forces from the valve 40 and from the cocking airflow, allowing the hammer 64 to return to the cocked position. Sufficient energy is also stored in the hammer spring 62 to allow this process to be repeated. Furthermore, the hammer 64 has sufficient kinetic energy to interact with the bolt 70 in such a way that it initiates the process or returns the bolt 70 to a state where it can hold the hammer in the cocked position, as will be described below.

[0110] In this embodiment, the hammer 64 contacts the valve stem 46 before it has completely passed through the outlet 69 to form the closed zone 65. The closing valve extension distance VED is greater than the closing distance CD to limit this loss under any other condition, namely, the hammer 64 is configured to pass through and close the gas outlet 69 before striking the valve stem 46.

[0111] Gun bolt: First implementation method

[0112] Figure 5 yes Figure 1 The right-side cross-sectional view of the air gun shows a first embodiment of the air gun having a bolt in the cocked position with the safety device disengaged.

[0113] exist Figure 5 In the illustrated embodiment, the bolt 70 has a firing control mechanism 76, a safety device 80, and a trigger 100. The firing control mechanism 76 interacts with the hammer system 60 to prevent the hammer 64 from firing. Figure 1 The indicated lever position will not be moved unless the user moves the safety device 80 from... Figure 1 The indicated engagement position is moved to Figure 2 The disengaged position is shown, and the trigger 100 is further disengaged from... Figure 1 The first trigger position shown is moved to Figure 5 The second trigger position is shown.

[0114] Now we will combine Figures 5-10 A more detailed description Figure 1 The operation of the implementation of the bolt action 70.

[0115] Figure 5 It shows Figure 1 The hammer system 60 and bolt 70 are shown in the right-side view in the cocked position, with the rest of the air gun 10 cut off.

[0116] like Figure 5As shown, in this embodiment, the safety device 80 has a safety pivot mount 82, which is mounted to the safety pivot 84 of the air gun 10. On the first side of the safety pivot mount 82 is a safety control surface 86, which is configured to interact with the user's finger so that the user can... Figure 5 The safety release position shown and Figure 1 The safety device 80 is moved between the safety engagement positions shown.

[0117] In this embodiment, the safety device 80 includes a safety stop surface 88 adapted to engage with a frame stop surface 90. The point where the safety stop surface 88 engages with the frame stop surface 90 prevents movement of the safety control surface 86, providing a tactile indication to a user moving the safety control surface 86 from the engaged position to the safety disengaged position, i.e., that the safety device 80 has reached the safety disengaged position.

[0118] As also shown in this embodiment, the safety device 80 has a hook 92 positioned on the side of the safety pivot mount 82 opposite to the safety control surface 86.

[0119] As described above, the trigger 100 has a trigger pivot mount 102 pivotally mounted to a trigger pivot 104 and a trigger control surface 106 configured to engage with a user's finger, allowing the user to... Figure 5 The lifting position shown and Figure 8 Move trigger 100 between the firing positions shown.

[0120] The trigger spring 110 is mounted around the trigger pivot 104 and applies a triggering force TF to bias the trigger 100 toward a non-firing position. The trigger spring has a primary sear bias leg 113 and a trigger reset contact leg 115, which, as described below, pushes the trigger 110 from the firing position to one or a series of non-firing positions.

[0121] The trigger 100 also has a trigger tab 112, which rotates together with the trigger 100 along the trigger tab path 114 when the trigger 100 moves from the non-firing position to the trigger firing position.

[0122] The locating pin 103 is positioned in the movement path of the trigger 100 to stop the movement of the trigger when or after the trigger 100 is moved to the trigger firing position.

[0123] The bolt 70 has a primary sear 120 that can move between a cocked position and a firing position. When the hammer 64 is in the cocked position, which is separated from the valve stem 46, the primary sear prevents the hammer 64 from moving along the hammer path 68, while in the firing position, it allows the hammer 64 to move along the hammer path 68 to contact the valve stem 46 and return from such contact.

[0124] exist Figure 6 In the diagram, the primary sear 120 is shown in the raised position and has a sliding pivot mount 122, which is pivotally and slidably mounted about a primary sear pivot 124. The primary sear 120 is configured and positioned by the primary sear pivot 124 such that the hammer engagement 126 is movably positioned between the raised position and the firing position. The hammer engagement 126 is configured to hold the hammer 64 in the raised position as long as the primary sear 120 is held in the raised position.

[0125] exist Figure 5 In one embodiment, the sliding pivot mount 122 is slidably mounted to the primary sear pivot 124 and is slidably movable in a series of positions near or away from the valve stem 46, and the primary sear bias leg 113 is configured to push the primary sear 120 in this direction.

[0126] The interaction between the sliding pivot mount 122 and the primary sear pivot 124 also limits the extent to which the primary sear 120 can slidably move from the hammer 64 toward the valve stem 46 in the cocked state. However, this interaction does not restrict the primary sear 120 from rotating about the primary sear pivot 124 along the first hammer engagement movement path 130 to a degree sufficient to remove the hammer engagement 126 out of the hammer path 68.

[0127] Conversely, in this embodiment, the hammer 64 and the hammer engagement 126 are configured to engage in such a way that the hammer engagement 126 rotates along the first hammer engagement movement path 130 in the first direction 161 until the hammer engagement 126 no longer obstructs the hammer 64 from traveling along the hammer path 68 to strike the valve stem 46. For example, and not limitingly, in this embodiment, the hammer 64 has a hammer face 67 configured to be substantially normal to the hammer path 68, with its tapered edge 72 facing the substantially complementary inclined hammer engagement 126. Thus, when the hammer spring force SF drives the hammer face 67 toward the valve 40 along the hammer path 68, the hammer face 67 interacts with the hammer engagement 126 to push the primary sear stop surface 128 of the primary sear 120 to rotate along the first hammer engagement movement path 130 in the first direction 161. Other mechanical arrangements can be used to achieve this result.

[0128] like Figure 6As shown, a secondary sear 140 is used to control whether the primary sear 120 can rotate along the movement path 130 of the first hammer engagement in response to the interaction of the hammer face 67.

[0129] exist Figure 6 In the diagram, the secondary sear 140 is shown in a raised position and has a secondary sear pivot mount 142, a head portion 150, and a tail portion 158. The secondary sear pivot mount 142 is mounted around a secondary sear pivot 144 for movement within a series of positions, including... Figure 2 As shown, the secondary sear 140 blocks the primary sear 120 from rotating in response to the force applied by the hammer 64 to the hammer latch 126.

[0130] exist Figure 6 An optional first direction limiter 160 is also shown, which limits the range of rotation of the head portion 150 and the secondary sear 140 in a first direction 161. In this embodiment, the first direction limiter 160 has a fixed spring mount 162 that positions the fixed spring 164 in the head rotation path 166 of the head portion 150 of the secondary sear 140 as the secondary sear 140 rotates about the secondary sear pivot 144 in the first direction 161. The fixed spring mount 162 and the fixed spring 164 are configured and positioned such that when the head portion 150 of the secondary sear 140 reaches a first position in the head rotation path 166 of the head portion 150, the fixed spring 164 begins to resist rotation in the first direction in order to provide a generally monotonically increasing resistance to the first direction rotation of the head portion 150 until sufficient force is applied to stop further movement of the head portion 150 along the head rotation path 166 in the first direction 161.

[0131] exist Figure 6 Further illustrated is one embodiment of the second direction limiter 170. In this embodiment, the second direction limiter 170 has a fixing screw mount 172 that positions a fixing screw 174 to control the degree of rotation of the tail portion 158 along the tail rotation path 176 in the second direction 163, at which time the secondary stop 140 is rotated to cause this movement of the tail portion 158. The fixing screw mount 172 and the fixing screw 174 are configured and positioned such that when the tail portion 158 of the secondary stop 140 moves along the tail rotation path in the first direction and reaches a first position in the tail rotation path 176, a portion of the fixing screw 174 blocks further movement of the tail portion 158.

[0132] Either the first direction limiter 160 or the second direction limiter 170 can be optionally adjusted by a user or service technician, and the air gun 10 can provide, for example, external access to the first direction limiter 160 and the second direction limiter 170.

[0133] In this embodiment, the secondary sear 140 has a lifting pivot 184 as shown in this embodiment for connecting with the tail portion 158 for movement.

[0134] The lifting member 180 has a lifting pivot mount 182 connected to a lifting pivot 184 for pivoting about the lifting pivot 184. The lifting pivot 184 is also connected to the tail portion 158 of the secondary sear 140. Therefore, when the lifting member 180 moves relative to the secondary sear 144, the tail portion 158 of the secondary sear 140 rotates about the lifting pivot 184, and when the lifting member 180 moves, the tail portion 158 of the secondary sear 140 does not rotate about the secondary sear 144.

[0135] The lifting member 180 has a lifting slot 186, which is shaped and positioned relative to the lifting member pivot 184 to engage with the trigger tab 112 when the trigger 100 is moved to transition the bolt 70 from the cocked position to the firing position of the air gun 10, so as to move together with the trigger tab.

[0136] Figure 7 A partial right-side cross-sectional enlarged view of the air gun 10 is shown, illustrating a partial view of the primary sear 120, the sliding pivot mount 122, the primary sear pivot 124, and the secondary sear 140, the secondary sear pivot mount 142, the secondary sear pivot 144, the head portion 150, and the secondary sear stop surface 152, all in their respective raised positions.

[0137] like Figure 7 As shown, the sliding pivot mount 122 has a first end 132 and a second end 134, the shapes of which selectively correspond to the shape of the primary sear pivot 124. The sliding distance SD separating the first end 132 and the second end 134 is greater than the diameter D of the primary sear pivot 124.

[0138] In the raised position, the spring force SF presses the hammer 64 against the hammer latch 126 to push the primary sear 120 to slide, thereby making the first end 132 contact the primary sear pivot 124.

[0139] The primary sear pivot 124 provides a holding force HF to prevent further movement of the primary sear 120 toward the valve stem 46. It will also be observed that when the first end 132 of the sliding pivot mount 122 is positioned against the primary sear pivot 124 as shown, the primary sear 120 is positioned to rotate about the primary sear pivot 124 along a first hammer engagement movement path 130, which overlaps with the edge 153 of the secondary sear stop surface by an overlap distance OD, to prevent the primary sear stop surface 128 from moving along the first hammer engagement movement path 130 in the first direction 161 when the primary sear 120 and the secondary sear 140 are in the flip-up position.

[0140] In various embodiments, the overlap distance OD can be equal to the difference between the diameter D of the primary sear pivot 124 and the sliding distance SD. In various embodiments, the overlap distance OD can be less than the difference between the diameter D of the primary sear pivot 124 and the sliding distance SD.

[0141] In this configuration, the secondary sear 140 prevents the primary sear 120 from rotating in the first direction along the movement path 130 of the first hammer engagement portion until the secondary sear stop surface 152 moves from the raised position to the firing position. The secondary sear 140 is biased toward the raised position by the secondary sear biasing member 154.

[0142] Figure 8 It shows Figure 1 A right-side cross-sectional view of the hammer system 60 and bolt 70 after they have responded to the trigger 100 moving to the trigger firing position. (See attached image.) Figure 8 As shown, when the user applies a trigger pull force (TPF) greater than the trigger force (TF) to the trigger control surface 106, the trigger 100 is released from the trigger. Figure 7 and Figure 8 The trigger in the non-firing position shown moves to Figure 9 The launch position is shown.

[0143] When the trigger 100 is moved to the firing position, the trigger tab 112 moves along the trigger tab path 114 in the first direction while remaining engaged with the trigger tab 112. Therefore, the movement of the trigger 100 from the engaged position to the firing position has the effect of pushing the lifting member 180 to move along the lifting path 190.

[0144] Furthermore, since the lifting member 180 is connected to the tail portion 158 of the secondary sear 140, movement of the lifting member 180 along the lifting path 190 causes the secondary sear 140 to rotate about the secondary sear pivot 144. This rotation drives the secondary sear stop surface 152 away from the first hammer engagement movement path 130, allowing the primary sear 120 to rotate from the lever position to the firing position. This occurs when the secondary sear 140 is rotated such that the edge 153 of the secondary sear stop surface is advanced at least one overlap distance OD towards the valve stem 46.

[0145] In this embodiment, the primary sear stop surface 128, the primary sear side surface 129, and the secondary sear stop surface edge 153 are shaped and positioned such that the hammer 64 can quickly rotate the hammer latch 126 out of the hammer path 68 to strike the valve stem 46, as described in more detail above.

[0146] like Figure 8 As shown, and as discussed in more detail above, the first hammer lifting force HCF1 is provided by the lifting flow 57, and the second hammer lifting force HCF2 is provided by the valve stem 46 against the hammer 64 to push the hammer 64 away from the valve stem 46. At the point shown in the figure, the sum of the first hammer lifting force HCF1 and the second hammer lifting force HCF2 exceeds the spring force SF applied by the hammer spring 62, so that the hammer 64 can subsequently be pushed back toward the lifting position.

[0147] Figure 8 It shows Figure 1 A right-side cross-sectional view of the air gun 10 according to the embodiment, showing the first hammer lifting force ( Figure 8 (not shown in the image) and second lifting force ( Figure 8 (Not shown) After being applied to hammer 64 for a period of time sufficient to push hammer 64 along hammer path 68 in the lifting direction to impart hammer lifting kinetic energy HCKE to hammer 64. Hammer lifting kinetic energy HCKE is sufficient to overcome the spring force SF experienced by hammer 64 in the series of positions it travels through as it returns to the lifting position.

[0148] It can be noted that as the hammer 64 moves toward the hammer spring 62, the hammer 64 passes through the hammer latch 126. As the hammer 64 travels toward the valve stem 46 during firing, the hammer latch 126 is rotated out of the hammer path 68 and can be held in this state so that the hammer 64 can pass through the hammer latch 126 without contact when it returns to the lever position.

[0149] However, it will also be noted that in this embodiment, when the trigger 100 is in the firing position, the primary sear can rotate freely about the primary sear pivot 124. Therefore, in some cases, the primary sear 120 may at least partially move back into the hammer path 68 before the hammer 64 moves past the hammer engagement.

[0150] In various embodiments, the hammer engagement 126 may have a hammer engagement deflection surface 127, which is shaped to interact with the return surface 74 of the hammer 64 such that when the primary sear 120 is in the position relative to the hammer engagement 126 as the hammer 64 returns toward the cocked position, the return surface 74 will drive the hammer engagement 126 away from the hammer channel 68. Using the hammer engagement deflection surface 127 helps ensure that the hammer engagement 126 is not damaged by the movement of the hammer 64 in these situations, and that the interaction with the hammer engagement 126 does not consume a large amount of hammer cocking kinetic energy (HCKE) to prevent the hammer 64 from returning to a position that would allow the hammer to be held in the cocked position.

[0151] However, in order to keep the hammer 64 in the raised position, it is necessary to return the bolt 70 to the raised configuration before the hammer 64 is pushed past the hammer latch 126 by the valve spring force VSF. To ensure proper timing or sequence, it is important that the bolt 70 is triggered to return to the raised configuration when the hammer 64 is within a specific position range within the hammer path 68.

[0152] Therefore, in the illustrated embodiment, the primary sear 120 also has a primary sear return surface 138 that enters the hammer path 68 and engages the hammer 64 when the hammer 64 is cocked and located within a series of positions in the hammer path 68. This engagement causes the bolt 70 to begin the process of returning to the cocked configuration, thus completing the process when it is necessary to hold the hammer 64 in the cocked position.

[0153] In this embodiment, the primary sear 120 is configured and mounted such that when the primary sear return surface 138 is positioned in the hammer path 68, the primary sear return surface 138 is positioned to receive energy from the hammer 64, and this energy can be used to rotate the primary sear 120 to move the hammer latch 126 into the hammer path 68.

[0154] Conversely, the hammer engagement 126 is configured such that when the primary sear 120 is released from engagement with the secondary sear stop surface 152, it allows the primary sear 120 to rotate along the first hammer engagement movement path 130. During firing, the engagement between the hammer face 67 and the hammer engagement deflection surface 127 pushes the hammer engagement 126 away from the hammer path 68, while simultaneously pushing the primary sear return surface 138 into the hammer path 68. Here, this is achieved by positioning the primary sear return surface 138 on the opposite side of the sliding pivot mount 122 relative to the hammer 126.

[0155] Now refer to Figure 9 and Figure 10 To describe this process. Figure 9 yes Figure 6 A partial enlarged cross-sectional view of the right side of the hammer system 60 and bolt 70, in which the hammer 64 moves in the lifting direction to make contact with the deflection surface of the primary sear. Figure 10 yes Figure 6 A partial cross-sectional enlarged view of the right side of the hammer system 60 and bolt 70, where the hammer 64 is moving toward the return position, where the spring force SF and the lifting force CF are approximately equal, to end the movement of the hammer 64 in the lifting direction.

[0156] like Figure 9 and Figure 10 As shown, the hammer 64 has a return surface 74, which is positioned to receive and be moved by the primary sear return surface 138 as the hammer 64 moves along the hammer path 68 in the cocking direction. The hammer return surface 64 and the primary sear return surface 138 are co-designed, so the interaction between these surfaces causes the bolt 70 to begin the process of returning to the cocking configuration.

[0157] In this embodiment, the hammer return surface 74 is curved, while the primary sear return surface 138 is inclined, such that the hammer return surface 74 interacts with the primary sear return surface 138 to push the primary sear 120 to slide and pivot, as will be described herein.

[0158] The sliding motion resulting from this interaction drives the primary sear mount 122 to move such that the second end 134 of the sliding pivot mount 122 contacts the pivot 124. The pivot 124 resists this motion by generating a second holding force HCF2, which overcomes the force generated by the interaction between the return surface 74 and the primary sear return surface 138.

[0159] exist Figure 10It will also be noted that when the second end 134 of the sliding pivot mount 122 is positioned against the primary sear pivot 124 as shown, the primary sear 120 is no longer positioned such that the primary sear stop surface 128 rotates around the primary sear pivot 124 along the first hammer engagement movement path 130. Instead, this rotation occurs along the primary sear return path 131, which is offset from the first hammer engagement movement path 130 by a certain offset distance, so as to provide the required amount of clearance between the primary sear 120 and the secondary sear 140 when the primary sear 120 rotates.

[0160] The rotation of the primary sear 120 repositions the hammer latch 126 in the hammer path 68 and can move the primary sear 120 out of a position that might interfere with the rotation of the secondary sear 140 to the first hammer latch movement path 130.

[0161] The rotation of the primary sear 120 also causes the primary sear surface 139 to contact the lifting ramp 189. This contact causes the lifting member 180 to rotate in such a way that the trigger slot 186 disengages from the trigger tab 112. This disengagement allows the secondary sear 140 to rotate in response to the push of the lifting spring 194 until the lifting member 180 is brought to the resting position against the locating pin 103.

[0162] In various embodiments, other arrangements may be used such that at least one of the primary sear 120 and the secondary sear 140 moves relative to the other of the primary sear 120 and the secondary sear 140 to provide a primary sear return path 131 different from the first hammer engagement movement path 130. In various embodiments, such sliding movement of the primary sear 120 may not be necessary.

[0163] In various embodiments, at least one of the primary sear 120 and the secondary sear 140 may move relative to the other of the primary sear 120 and the secondary sear 140 along a nonlinear path and at least partially not parallel to the hammer path 68.

[0164] Generally, hammer 64 reaches its return position when it exhausts its hammer-plate starting energy to the point where it can no longer generate a force greater than that exerted by hammer spring 62. This occurs when the spring force SF resisting the movement of hammer 64 is greater than the force that hammer 64 can generate with its remaining hammer-plate starting energy (HCKE). Figure 10 In the embodiment shown, this occurs after the hammer 64 has moved through in the lifting direction. Figure 6 When the launch position is shown.

[0165] Subsequently, the spring force SF eventually overcame the lifting force CF, causing hammer 64 to... Figure 9 Move to the position shown Figure 10 Move to the position shown, and then move to the position indicated. Figure 5 The location shown.

[0166] As the primary sear 126 is first driven to contact the hammer 64, the hammer 64 first pushes the primary sear 120 to slide so that the first end 132 of the sliding pivot mount 122 contacts the primary sear pivot 124. This then causes the primary sear to rotate about the primary sear 120 along the first hammer engagement movement path 130. Subsequently, the hammer 64 abuts against the hammer engagement 126, which pushes the primary sear 120 forward to a degree not yet achieved by the bias force applied by the trigger spring, and rotates along the first hammer engagement movement path 130, as described above for... Figure 5 As stated above.

[0167] As in Figure 5 As described in the text, this movement is now blocked by the secondary sear 140 present in the hammer engagement movement path 130 until the trigger 100 rotates under the action of the trigger return spring 111 until the trigger tab 112 re-engages the trigger slot 186. This occurs when the user releases the trigger 100 or reduces the trigger pull on the trigger 100.

[0168] Refer again Figure 3 The hook 92 of the safety device 80 is positioned and configured to be in a disengaged position separate from the secondary rail 140 and Figure 1 The movement between the engagement positions shown, wherein the hook 200 engages with a common design feature 202 on the secondary sear 140 to prevent the secondary sear 140 from being moved such that the secondary sear stop surface 152 moves from the first hammer engagement movement path 130.

[0169] Figure 11 A top view of one embodiment of the secondary sear 140 and a portion of the safety device 80 is shown. In this embodiment, the secondary sear 140 includes a right wall 212 and a left wall 214 connected by a lifting pivot 184, a secondary sear pivot 144, and a column 210. In this embodiment, the lifting pivot 184 is positioned to engage by a hook 92 such that rotation of the secondary sear about the secondary sear pivot 144 is blocked when the safety device 80 is in the engaged position.

[0170] In this manner, a gas-powered launch control system 70 is provided, which can release a substantially preset amount of pressurized gas sufficient to propel the projectile 26 through the chamber 16 toward the target. Furthermore, when the user moves the trigger 100 to the firing position, the gas-powered launch control system 70 automatically returns to a state where it is ready to release a substantially preset amount of pressurized gas a second time.

[0171] Gun bolt: Second implementation method

[0172] Figure 12 This is a right-side view of another embodiment of the bolt carrier 70. To better illustrate the described concept, a portion of the secondary sear 140 and the secondary sear spring have been removed. Figure 13 yes Figure 12 Front, right, and top perspective views of an embodiment of the bolt carrier 70.

[0173] In this embodiment, the trigger 100 is mounted around the trigger pivot 104 and is connected to the first end 117 of the lifting member 116 via the trigger lifting member pivot 118.

[0174] The trigger return spring 111 is also mounted around the trigger pivot 104. The trigger return spring 111 has a primary sear bias leg 113 and a secondary spring, namely the trigger reset contact leg 115, which pushes the lifting member 116 to rotate around the trigger lifting member pivot 118, causing the first lifting end 121 to contact the trigger stop 108. When the first lifting end 121 contacts the trigger stop 192, this pushing action will push the trigger 100 away from the firing position.

[0175] In this embodiment, and as described above, the primary sear 120 is slidably and pivotally mounted to the primary sear pivot 124, and has the function of holding the hammer 64 in place. Figure 12 The hammer latch 126 is shown in the cocked position. The primary sear 120 is rotatable about the movement path 130 of the first hammer latch, and the hammer latch 126 is rotatable out of the cocked position to release the hammer 64 for firing, as generally described above.

[0176] In this embodiment, the primary sear bias leg 113 may optionally press against the sliding pivot mount 122 to push the primary sear 120 to move along the primary sear pivot 124, so that the hammer engagement 126 is positioned to rotate about the first hammer engagement movement path 130.

[0177] As described above, a secondary sear 140 is provided, which is rotatable about a secondary sear pivot 144 in a second direction from a position in which the secondary sear 140 blocks the rotation of the primary sear 120 along the first hammer engagement movement path 130, thereby preventing the hammer 64 from passing through the hammer engagement 126 unless the secondary sear 140 is moved from the first hammer engagement movement path 130.

[0178] The first direction limiter 160 is shown here in the form of a fixed spring mount 162 and a fixed spring 164. The fixed spring 164 applies an increasing force to push the secondary sear 140 to rotate in the first direction 161, thereby effectively limiting the movement of the primary sear 120 in the second direction 163.

[0179] The secondary sear engagement surface 141 is associated with the secondary sear 140 such that, in this embodiment, movement of the secondary sear engagement surface 141 causes pivoting movement of the secondary sear 140. Therefore, the secondary sear engagement surface 141 is movable about the secondary sear pivot 144 along an arcuate secondary sear engagement surface path 143. Here, the secondary sear engagement surface 141 is positioned on the tail portion 158 of the secondary sear 140, but in other embodiments, the secondary sear engagement surface 141 may be located elsewhere.

[0180] like Figure 12 and Figure 13 As shown, the trigger reset lift 116 is positioned by the trigger 100 such that the second lifting end 123 of the trigger reset lift 113 contacts the secondary sear engagement surface 141 when the trigger 100 is in a series of positions including a series of non-firing positions.

[0181] like Figure 13 As shown, an optional secondary sear spring 146 provides a biasing force that drives the secondary sear 140 to rotate in a first direction 161 so as to bias the secondary sear engagement surface 141 to remain engaged with the second lifting end 123 of the trigger lift 113.

[0182] In order for the air gun 10 to fire, the user pulls the trigger 100 through a series of non-firing positions. This causes the trigger 100 to rotate, which in turn causes the trigger return lift 116 to rotate along the trigger lift path 119. Here, the trigger lift path 119 extends in an arc around the trigger pivot 104.

[0183] from Figure 14 As can be seen, when the trigger 100 is moved past the first range position, the secondary sear engagement surface path 143 and the trigger lifting path 119 are substantially coincident. Therefore, moving the trigger 100 past this first range position causes the secondary sear 140 to move in the second direction 163. Ultimately, this will cause the secondary sear 140 to move to a position that does not obstruct the movement of the primary sear 120 along the hammer movement path 130, thereby releasing the hammer 64 and causing the air gun 10 to fire.

[0184] Once the primary sear 120 is released from this constraint, forces such as those exerted by the hammer spring 62 and the hammer 64 on the hammer latch 126 will drive the primary sear 120 to rotate out of the hammer path 68, allowing the hammer 64 to open and close the valve 40.

[0185] In addition, such as Figure 14 As shown, when or after the trigger 100 is pulled to the firing position, the degree to which the second sear engagement surface path 143 diverges from the trigger lifting path 119 is sufficient to cause the second lifting end 123 of the lifting member 116 to separate from the second sear engagement surface 141.

[0186] When this occurs, the secondary sear spring 146 pushes the secondary sear 140 to rotate in the first direction 161, causing the secondary sear engagement surface 141 to return to its original position. Figure 12 and Figure 13 The location shown.

[0187] Finally, as described in more detail above, hammer 64 returns along hammer path 68 and strikes primary sear return surface 138. This causes primary sear 120 to be driven so that secondary sear 140 can rotate in first direction 161 and be repositioned to hold primary sear 120 in the position where hammer latch 126 holds hammer 64 in the cocked position.

[0188] Then, trigger 100 must return to a series of non-firing positions. When the user releases the trigger, trigger bias spring 110 pushes lift member 116 and trigger 100 toward... Figure 12 and Figure 13 The position is moved as shown. However, at this time, the second lifting end 123 of the lifting member 116 cannot follow the trigger lifting path 119 because the second sear engagement surface 141 is pre-positioned in the trigger lifting path 119. However, when the second lifting end 123 contacts the secondary sear engagement surface 141, the lifting member 116 pivots against the biasing force of the trigger return spring leg 115, so that when the trigger 100 is returned to a series of non-firing positions, the second lifting end 123 follows the shunt path 147 around the secondary sear engagement surface. When the trigger 100 moves further away from the firing position, reaching the end of the shunt path 147, the trigger return contact leg 115 of the trigger spring 110 biases the trigger return lifting member 116, causing it to return to the trigger lifting path 119, so that on the next trigger pull, the second lifting end 123 is positioned to drive the secondary sear engagement surface 141.

[0189] Reinstalling the system

[0190] As mentioned above, the semi-automatic operation of the air gun 10 also conventionally means that after the first projectile 26 is fired, another projectile is positioned for firing without user intervention. This is known as the automatic reloading process.

[0191] Ideally, the automatic reloading process should be performed at least partially during the time it takes for the hammer 64 to return to the cocked position or for the bolt 70 to return to the firing configuration, or both. This has the effect of reducing the amount of time required between the firing of one projectile 26 from the air gun 10 and the firing of another projectile 26 from the air gun 10.

[0192] Furthermore, it is highly desirable that such a reloading process be performed without necessary mechanical interaction with the hammer system 60, without necessary mechanical interaction with the bolt 70, without imposing additional requirements on the stored compressed air, and without diminishing the performance of other systems in the air gun 10.

[0193] Furthermore, preferably, such a process does not involve the use of additional electronic controls, electromechanical actuators, or mechanical subsystems, all of which would significantly increase the complexity, cost, or weight of the air gun 10.

[0194] Now refer to Figures 15-18 Describe the automatic loading process used in the air gun 10. Figure 15 yes Figure 1 A partial cross-sectional view on the right side of an embodiment of the medium air gun 10, with the bolt 24 in the firing position. Figure 16 This is a right-side cross-sectional view of one implementation of the reloading system when the trigger is just pulled to the firing position and the bolt is in the firing position. Figure 16 yes Figure 15 The enlarged view of the indicated part.

[0195] Figure 17 yes Figure 1 A partial cross-sectional view on the right side of an embodiment of the air gun 10, with the bolt 24 in the returned position. Figure 18 yes Figure 1 The right-side cross-section and sectional view of the embodiment shows the bolt 24 in the position engaged with the projectile 26 during loading.

[0196] As described above, the projectile loading system 18 has a retainer 22 that holds and interacts with the removable projectile storage system 20 so that one of the plurality of projectiles 26 is positioned in the loading area 21 from which the projectile 26 can advance through the loading area and through the chamber 16 for firing.

[0197] As described above, the loading area 21 is shown located between the bolt-side opening 25 and the bore-side opening 27 of the projectile storage system 20. In the illustrated embodiment, the projectile storage system 20 and the projectile storage system locator 22 are configured such that the loading area 21, the bolt-side opening 25, and the bore-side opening 27 are substantially aligned with the bolt tip portion 240 and the bore 16 to allow at least a portion of the bolt 24 to enter and exit the loading area 21 when the projectile storage system 20 is properly positioned in or otherwise mechanically associated with the projectile storage system retainer 22.

[0198] exist Figures 15-18 In this system, the projectile storage system 20 has multiple projectile holders 23, which are biased to move in a manner that causes a projectile 26 to be positioned in the loading zone 21. The projectile storage system 20 is also configured such that this biasing movement of the projectile holders 23 can be blocked by the presence of the bolt 24 in the loading zone 21, or by the presence of a projectile 26 in the loading zone 21. Therefore, during a reloading operation, the biasing movement of the projectile holders 23 to position a new projectile 26 only occurs when the loading zone 21 is free of the bolt 24, and must be completed before the bolt 24 returns to its original position.

[0199] The movement of the bolt 24 is constrained by the bolt drive system 220, which provides the bolt path 250, allowing the bolt 24 to... Figure 15 and Figure 16 The launch position shown Figure 17 The return position shown and Figure 18 The bolt 24 moves between the indicated engagement positions. The bolt 24 has a bolt body portion 230 and a bolt tip portion 240 extending a predetermined length from the bolt body portion 230.

[0200] exist Figures 15-18 In this embodiment, the bolt 24 is biased to move into the firing position by the action of the bolt drive system 220. In the illustrated embodiment, the bolt drive system 220 includes a resilient compression bolt spring 252 that engages with the bolt 24 on the side of the bolt body portion 230 opposite to the side where the bolt tip portion 240 is located. Other configurations are possible, including, but not limited to, implementations utilizing tension or other types of springs.

[0201] like Figure 15As shown, the bolt tip portion 240 is sized and shaped such that, when the bolt 24 is in the firing position, it extends through the bolt side opening 25, the projectile retainer 23, the chamber side opening 27, through the bolt seal 28, and into the chamber 16. The bolt seal 28 and the bolt tip portion 240 are designed together to be releasable, which generally restricts the flow of power 55 in the direction away from the projectile 26. Therefore, during firing, an accumulation cavity 56 is formed between the chamber 16, the bolt tip portion 240, the projectile 26, and the bolt seal 28.

[0202] like Figure 16 As shown in the optimal configuration, in the firing position, the bolt tip portion 240 extends over the transmission tube 58 and provides a channel 241 that allows power flow 55 to be transmitted partially along a portion of the length of the bolt tip portion 240 to an opening 243 in the bolt face 245. The size and shape of the bolt face 245 engage with the projectile 26, so that movement of the bolt face 245 against the projectile 26 can move the projectile 26 as required to position it for firing through the chamber 16.

[0203] In various embodiments, the size of the bolt face 245 is designed to distribute the forces applied to the projectile over a large diameter around the outer periphery of the projectile. This helps to distribute the driving load more evenly around the periphery of the projectile during loading and reduces the possibility of pitch or yaw misalignment of the projectile 26 relative to the bore side opening 27, the bolt seal 28, or the bore 16.

[0204] As generally described above, when the hammer 64 strikes the valve stem 46, a power flow 55 begins to flow into the accumulator cavity 56, where it is trapped between the chamber 16, the projectile 26, the bolt seal 28, and the bolt tip portion 240. This creates gas pressure on all surfaces forming the accumulator cavity 56. As the power flow 55 continues, this pressure rapidly increases until it reaches the firing pressure, at which point the projectile 26 is propelled through the chamber 16, causing it to exit the chamber 16 at at least a minimum velocity.

[0205] To help ensure that the pressure in the accumulator cavity 56 builds up to the firing pressure, it is important that the accumulator cavity 56 does not expand significantly during the pressure buildup period as the power flow 55 increases the pressure within it. Therefore, it is well known that the bolt of a conventional air gun is fixed during pressure accumulation. Consequently, such air guns cannot effectively utilize the high pressure generated during firing during reloading, requiring a mechanism to hold the bolt in place during firing.

[0206] However, in the air gun 10, a method has been found that allows an ideal high firing pressure to be achieved in the accumulation cavity 56 during firing, and that a mechanism for fixing the bolt 24 is not required during such firing, while also allowing the high firing pressure to serve a dual purpose, namely firing the projectile 26 through the chamber 16 and setting the movement of the bolt 24 for reloading.

[0207] Accordingly, the bolt drive system 220 can be configured to keep the bolt 24 substantially stationary for a period of time sufficient to allow the power flow 55 to provide the force required to fire the projectile 26 through the chamber 16 at the desired velocity, while simultaneously retracting the bolt 24 from the chamber 16 and the projectile loading system 18 for a period of time sufficient to allow the projectile loading system 18 and the projectile storage system 20 to position the projectile 26 in the loading area 21, from which the bolt 24 can then cause the projectile 26 to be repositioned for firing from the chamber 16.

[0208] Furthermore, the bolt drive system 220 should achieve these results without significantly increasing the cost, complexity, or weight of the air gun 10 or causing a significant increase in the amount of compressed gas used during firing and reloading.

[0209] The initial problem arose from the challenge of keeping the bolt 24 essentially in the firing position during firing, while still allowing it to move during the loading operation.

[0210] Because the projectile 26 and the bolt tip 240 have similar (if not identical) cross-sectional areas, the pressure generated by the power flow 55 exerts substantially equivalent forces on the bolt 24 and the projectile 26. Ultimately, these forces overcome the kinetic resistance of the bolt 24 and the projectile 26.

[0211] One of the characteristics that determines the drag force of the bolt 24 and the projectile 26 is their resistance to changes in their state of motion. This is called inertia. Generally speaking, the inertia of an object is proportional to the mass of that object.

[0212] In this embodiment, the bolt 24 is configured to have a much larger mass than the projectile 26, and therefore experiences greater resistance to changes in its motion. The bolt 24 is designed to have a mass many times greater than that of the projectile 26. For example, in various embodiments, the mass of the bolt 24 can be 15 to 300 times the mass of the projectile 26. In the illustrated embodiment, the mass of the bolt 24 is approximately 40 to 50 times that of the projectile 26. Other proportions may be used in other embodiments.

[0213] Acceleration is governed by the following formula: Acceleration = Force / Mass. Here, the forces acting on the bolt 24 and the projectile 26 are essentially equal. Therefore, when the firing pressure reaches its peak, the mass difference determines the difference in their respective accelerations, with the bolt 24 experiencing an acceleration approximately 1 / 40-1 / 50th that of the projectile 26. In other embodiments, the mass of the bolt can be 20-400 times that of the projectile 26.

[0214] Therefore, at the critical moment of reaching the firing pressure, the bolt 24 moves almost or not at all relative to the projectile 26 because a large amount of inertia must be overcome to move the bolt 24. Other factors, such as friction, the spring force acting on the bolt 24, and the need for the projectile 26 to align with the possibly rifling chamber 16, can all affect the final velocity of the bolt 24 and the projectile 26.

[0215] Subsequently, the movement of the projectile 26 along the chamber 16 causes the accumulation cavity 56 to expand to a degree far exceeding any expansion caused by the movement of the bolt 24. Therefore, as the projectile 26 passes through the chamber 16, the effect of the movement of the bolt 24 on the pressure experienced by the projectile 26 becomes increasingly smaller.

[0216] Furthermore, the high force generated by the firing pressure is used to overcome the static inertia of the bolt 24 and any other forces opposing the movement of the bolt 24 during firing. These opposing forces cause the bolt 24 to be driven along the first direction 256 with inertia in the first direction and initial bolt kinetic energy, which is then used to drive the bolt 24 in a manner capable of reloading the projectile 26 into the chamber 16, as will be described herein. Thus, the energy generated by the kinetic flow 55 is used to accelerate the bolt 24 and the projectile 26, while the additional demand for pressurized gas, if any, is negligible.

[0217] Furthermore, in each embodiment, the mass of the bolt 24 is selected so that the bolt 24 does not move past the bolt seal 28 until the exit of the projectile 26 relative to the chamber 16 is within a predetermined position range.

[0218] like Figure 18 As shown, the power flow 55 drives the bolt 24 to leave the chamber 16 along the first direction 256 and begins to drive the bolt 24 to leave the loading area 21 in the projectile loading system 18.

[0219] The initial bolt kinetic energy IBKE in the first direction 256 must be exhausted so that the bolt 24 can return to the loading position in the second direction 258.

[0220] exist Figure 15-18In this embodiment, the bolt drive system 220 absorbs the kinetic energy of the bolt 24 as the bolt 24 moves along the first direction 256 to stop the movement of the bolt 24 in the first direction 256, and stores a portion of the initial bolt kinetic energy IBKE as bolt return potential energy BRPE, which can be released to allow the bolt 24 to return along the second direction 258, so that the projectile 26 can move from the loading area 21 through the bolt 24.

[0221] like Figure 17 As shown, the bolt drive system 220 is also configured such that, as the bolt 24 travels to the return position, the bolt 24 is moved to a position where it does not occupy the loading area 21. This allows the projectile loading system 18 to initiate the process of moving at least one projectile mount 23 in the projectile feeder 20 to position the projectile 26 in the loading area 21.

[0222] The process of moving the projectile 26 into the loading area 21 requires some time to complete. Therefore, the bolt drive system 220 must provide a projectile positioning delay between the movement of the bolt 24 away from the projectile loading area 21 in the first direction 256 and the movement of the bolt 24 into the loading area 21 in the second direction 258.

[0223] Furthermore, preferably, the bolt 24 returns through the loading area 21 in the second direction 258 at a speed likely much lower than when it initially moves in the first direction 256. This is to ensure that features of the projectile 26, such as the flexible skirt feature on an air gun projectile, are not potentially damaged when pushed in from the loading area 21 by the bolt 24, and to ensure that the projectile 26 is ideally positioned for firing.

[0224] Finally, it is understandable that this result is achieved in managing the movement of the moving bolt 24, which has a large mass and therefore a large amount of inertia and kinetic energy to manage.

[0225] exist Figures 15-18 In the embodiment shown, the bolt drive system 220 uses a combination of bolt spring 252, buffer spring 272, and forward assist device 270 to control the movement of the bolt 24.

[0226] In this embodiment, the bolt path 250 has an end wall 251 with an opening 243 through which the forward assist device 270 is positioned, and both the bolt spring 252 and the buffer spring 272 are shown as compressible helical springs.

[0227] The forward assist device 270 has a bolt spring positioner 274, which is sized and shaped to engage the coil of the bolt spring 252, and the bolt 24 has a bolt spring engagement surface 244, which is sized and shaped to engage the coil of the bolt spring 252. The bolt spring 252 is located in the bolt path 250, between the bolt spring engagement surface 244 and the coil of the bolt spring 252 (between the bolt spring engagement surface 244 and the buffer spring positioner 276), to provide an elastic biasing force that pushes the bolt 24 away from the bolt spring positioner 274.

[0228] The bolt 24 also has a forward auxiliary engagement surface 248 that extends a predetermined length 249 in a first direction 256 away from the bolt spring engagement surface 244, around which the elastically compressed bolt spring 252 can be positioned, and this length provides an optional spring guide surface for the bolt spring 252.

[0229] The forward assist device 270 further includes a buffer spring positioner 276, sized and shaped to engage the coil of the buffer spring 272 at one end, while the end wall 251 is sized and shaped to engage the coil of the buffer spring 272 at the other end. The buffer spring 272 is located in the bolt path 250, between the bolt spring engagement surface 244 and the coil of the bolt spring 252 (between the end wall 251 and the buffer spring positioner 276), to provide an elastic biasing force that pushes the buffer spring positioner 276 away from the end wall 251.

[0230] When the bolt 24 begins to move in the first direction 256 after firing, the bolt spring 252 elastically resists the movement of the bolt 24 in the first direction 256. The bolt spring 252 has a bolt spring coefficient and is configured to extend from the first bolt spring length 260 ( Figure 15 ) compressed to the second bolt spring length 264 ( Figure 17 The first part of the initial bolt kinetic energy IBKE in the first direction 256 is converted into the first part of the first bolt return potential energy BRPE1 stored in the bolt spring 252.

[0231] The buffer spring 272 elastically resists the movement of the buffer spring positioner 276 toward the end wall 251 when the bolt 24 moves in the first direction 256. This movement may be caused by the force exerted by the bolt spring 252 on the bolt spring positioner 274 or by the forward auxiliary engagement surface 248 on the forward auxiliary device 270.

[0232] In this embodiment, the buffer spring 272 extends from the length 266 of the first buffer spring. Figure 16The bolt is compressed to the length 267 of the second buffer spring (Fig. 19), and the second part of the initial bolt kinetic energy IBKE in the first direction 256 is converted into the second part of the bolt return potential energy BRPE, and a force is applied in the first direction 256 to decelerate the bolt 24.

[0233] In this embodiment, the spring constant of the buffer spring 272 is significantly higher than that of the bolt spring 252.

[0234] Therefore, in this embodiment, during the first portion of the movement of the bolt 24 along the first direction 256, the compression of the bolt spring 252 is greater than that of the buffer spring 272, and the resistance to the movement of the bolt 24 is smaller, allowing the bolt tip 240 to quickly clear the loading area 21, thereby initiating reloading.

[0235] As the bolt 24 continues to move in the first direction 256, the gap between the bolt spring engagement surface 244 and the bolt spring positioner 274 remains closed. Eventually, this gap closes to a point where the bolt spring 252 reaches a compression level, where further movement of the bolt 24 in the first direction 256 is primarily resisted by the deflection of the buffer spring 272, or the forward auxiliary engagement surface 248 contacts the forward auxiliary device 270, thereby stopping the compression of the bolt spring 252. Therefore, in this embodiment, the second bolt spring length 264 is substantially equal to the preset length 249 plus any length between the bolt spring engagement surface 282 and the bolt spring positioner 274.

[0236] The buffer spring 272 has a spring constant that is selected to allow the direction of the bolt 24 to reverse for a period of time as the movement of the buffer spring 272 in the first direction 256 is about to end, thereby reducing the impact and vibration experienced within the air gun 10.

[0237] The buffer spring 272 also has a spring constant, which is selected to store the second bolt return potential energy BRPE2 in the buffer spring 272. This potential energy, combined with the first bolt return potential energy BRPE1, is sufficient to drive the bolt 24 from... Figure 17 The return position shown is to Figure 18 The loading location and to Figure 15 and Figure 16 The launch position is shown.

[0238] In various embodiments, the spring constant of the buffer spring 272 is selected, at least in part, to extend the time required for the projectile supply system 18 to load a new projectile 26 into the loading area 21 over a given travel distance of the bolt 24 in the bolt path 250.

[0239] In some embodiments, by using an extended bolt spring or by allowing a rigid structure such as end wall 251 to absorb any movement of the bolt 24 in the first direction 256, the bolt spring 252 can return the bolt to the loading position and then advance the projectile 26 to a position where it can be fired from the chamber 16, thereby avoiding the use of a buffer spring. In various embodiments, this kinetic energy can be transferred directly or through intermediate structures (including, but not limited to, forward assist device 270) to the end wall 251.

[0240] However, in this case, the bolt 24 returns to the loading area 21 in a shorter time than in the loading area 21. Figures 15-18 In this embodiment, less time is required. In this embodiment, the buffer spring 272 is used to absorb this kinetic energy over time and return a portion of the kinetic energy to the bolt 24 after a period of time. The time required for the buffer spring 272 to do this increases the total time the bolt 24 is outside the loading zone 21, thereby providing more time for the projectile supply system 18 to place the projectile 26 into the loading zone 21.

[0241] After the bolt 24 is reoriented to travel along the second direction 258, the rate at which the bolt 24 returns to the loading position 21 and the chamber 16 is primarily controlled by the first bolt return potential energy BRPE1 released by the bolt spring 252 on the bolt 24. Due to the low spring coefficient of the bolt spring 252, the bolt is pushed to a speed suitable for moving through the loading zone 21, engaging the projectile 26, and positioning the projectile 26 in preparation for firing.

[0242] The lower spring coefficient of the bolt spring 252, the higher spring coefficient of the buffer spring 272, and the degree to which the bolt spring 252 and the buffer spring 272 are compressed during the movement of the bolt 24 in the first direction 256 are also selected so that the loading system 18 can, when the bolt 24 moves to the return position, the buffer spring 272 and the bolt spring 252 twist the direction of the bolt 24, and then the bolt spring 252 and the buffer spring 272 cause the bolt head 240 to return through the loading zone to the chamber 16 and... Figure 16 The projectile 26 will be moved to the loading area 21 within the time required for the launch position shown.

[0243] Furthermore, it is understandable that, since the mass of the bolt 24 is much greater than the mass of the projectile 26, the bolt 24 will have sufficient kinetic energy to help ensure that the projectile 26 is inserted into the chamber 16.

[0244] It can be understood that in the bolt drive system 220, the time and extent of displacement of the bolt spring 252 are functions of the separation distance between the bolt spring engagement surface 244 and the bolt spring positioner 274; similarly, the time and extent of displacement of the buffer spring 272 are functions of the separation distance between the end wall 251 and the buffer spring positioner 276. These variables can be adjusted to suit the needs of a specific system and requirements.

[0245] In various embodiments, the air gun 10 may be configured to receive one of a plurality of forward assist devices 270, each having a bolt spring positioner 274 and a buffer spring positioner 276, adapted to optimize the operation of the bolt drive system 220 for semi-automatic loading of different types of projectiles 26, projectile storage system 20, or pressure range of power flow 55.

[0246] In various embodiments, the bolt spring 252 and the buffer spring 272 may be stacked or connected together in other ways.

Claims

1. An air gun, comprising: A valve configured to release pressurized gas when the valve stem moves from a closed position and a series of open positions; The hammer, which is biased by the hammer spring, moves from the flip-up position along the hammer path to drive the valve from the closed position through the series of open positions, causing the valve to release the pressurized gas flow; The primary sear is movable between a primary sear raised position and a primary sear returned position. In the primary sear raised position, the primary sear hammer engagement part is located in the hammer path to hold the hammer in the hammer raised position. In the primary sear returned position, the primary sear return surface is located in the hammer path. The secondary sear is movable between the secondary sear up position and the primary sear firing position. In the secondary sear up position, it prevents the primary sear from moving from the primary sear up position. In the primary sear firing position, it allows the primary sear to move from the up position to the firing position, so that the hammer can strike the valve stem. The secondary sear spring biases the secondary sear toward the position where it is lifted up. The trigger is movable between a trigger-off position and a trigger-fire position; as well as The lifting element is movable between engaged positions, in which it mechanically connects the secondary sear to the trigger, such that as the trigger moves to the trigger firing position, the secondary sear moves to the secondary sear firing position, allowing the hammer to move the primary sear from the primary sear lift position to the primary sear return position. During launch, a portion of the gas released from the valve travels into the hammer path and drives the hammer along the hammer path away from the valve stem, causing the hammer to travel to the return position and drive the primary sear from the return position to the primary sear raised position; and After firing, the lifting mechanism disengages to allow the trigger and secondary sear to move separately, causing the secondary sear spring to move to the secondary sear raised position. This keeps the primary sear in the primary sear raised position before the hammer spring biases the hammer to move it from the return position to the raised position.

2. The air gun according to claim 1 further includes a pressurized gas supply device and a regulator, the regulator receiving pressurized gas from the supply device and supplying regulated gas to the valve.

3. The air gun according to claim 1, wherein, The lifting element is connected to the secondary sear, positioned between an engaged position that connects the secondary sear to the trigger for movement with the trigger and a disengaged position that allows for separation.

4. The air gun according to claim 3, wherein, The primary sear has a primary sear return surface. When the hammer latch is not in the hammer path, the primary sear return surface is moved into the hammer path, and when the hammer travels to the return position, the primary sear return surface is positioned to be driven by the hammer to move the primary sear, causing the hammer latch to return to the hammer path.

5. The air gun according to claim 4, wherein, The lifting member is connected to the secondary sear between the primary sear and the secondary sear, and is positioned such that movement of the primary sear's hammer catch returning to the hammer path causes the lifting member to pivot from the engaged position to the disengaged position.

6. The air gun according to claim 4, wherein, The lifting element is pivotally connected to the secondary sear, and the primary sear causes the secondary sear to rotate from the engaged position to the disengaged position.

7. The air gun according to claim 1, wherein, When the trigger is pulled, the lifting element is movable along the first path, while the secondary sear engagement surface is rotatable about the second path, which largely overlaps with the first path. As the trigger is pulled, the lifting element is positioned to drive the engagement surface through the overlapping portion, at least until the secondary sear moves to the secondary sear firing position.

8. The air gun according to claim 7, wherein, When the trigger is pulled past the overlapping part, the lifting element separates from the engagement surface of the secondary sear, and the secondary sear spring causes the secondary sear to return to the secondary sear raised position.

9. The air gun according to claim 8, wherein, As the trigger moves from the trigger firing position toward the trigger non-firing position, the lifting member is movable relative to the trigger, thereby enabling the lifting member to follow different second paths around the secondary sear engagement surface.

10. The air gun according to claim 9, wherein, The lifting component is biased and returns to the first path.

11. The air gun according to claim 1, further comprising an automatic reloading system, wherein, The bolt has a mass 40 to 50 times that of the projectile to be fired by the air gun.

12. The air gun according to claim 11, wherein, During firing, the bolt is not fixed.

13. The air gun according to claim 12, wherein, During firing, a portion of the pressurized gas released by the valve enters the cavity between the bolt and the projectile, accelerating the bolt to a first velocity and the projectile to a second velocity, which is at least 40 times the first velocity.

14. The air gun according to claim 13, wherein, The bolt passes through a seal into the chamber, and the chamber is partially sealed by the seal and the chamber. The bolt's velocity is selected such that it does not move past the seal before the gas pressure in the chamber reaches the firing pressure.

15. The air gun according to claim 14, wherein, The bolt is biased by the bolt spring and moves into the chamber. The firing pressure accelerates the bolt with sufficient kinetic energy, causing it to resist the biasing force of the bolt spring and travel a predetermined distance away from the chamber.

16. The air gun according to claim 11, wherein, The bolt extends through the loading zone of the projectile loading system, and the projectile loading system can load the projectile into the loading zone during the loading time when the loading zone is not blocked by the bolt and the projectile is not in the loading zone.

17. The air gun according to claim 16, wherein, The bolt mass, the length of the preset distance, and the bolt spring bias are selected to keep the bolt outside the loading zone during the retraction time, which is at least equal to the loading time.

18. The air gun of claim 16 further includes a buffer spring positioned between the bolt and an end wall of the bolt path in which the bolt moves, the spring constant of the buffer spring being determined in part to increase the length of the retraction time.

19. A method of operating an air gun according to any one of claims 1-18, comprising: The hammer latch is positioned in the cocked position. In the cocked position, the hammer latch is positioned to hold the spring-biased hammer in the cocked position. Position the secondary sear in the raised position to hold the hammer latch, thereby preventing the biased hammer from driving the hammer latch away from the raised position. The user pulls the trigger from a non-transmitting position to a transmitting position; In response to a received pull of the trigger by the user, the secondary sear is moved to the firing position. In the firing position, the secondary sear does not prevent the biased hammer from driving the hammer latch away from the raised position. In response to the hammer moving past the lever position, the valve opens to release the pressurized gas; Pressurized gas is used to make the hammer resist the deflection force and return to the return position; This disengages the movement of the secondary sear from the movement of the trigger. The movement of the hammer towards the return position is detected, and in response, the hammer latch is returned to the raised position and the secondary sear is moved to the raised position before the biased hammer has traveled from the return position to the hammer latch. Return the hammer to the non-firing position; as well as Reconnect the hammers.

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