EP2385337A2 - Recoil system for firearms - Google Patents

Abstract

The device (1) has a closure provided with a slidegate valve and adjusted between a closed starting position and an opened end position. A pressure control valve (20) is connected with a hydraulic chamber (13) that comprises a mobile separator piston (14). The piston separates the hydraulic chamber from a gas pressure chamber (17). A working piston closes the pressure control valve and opens an exhaust valve (30) in simultaneous or delayed manner. A hydraulic medium is guided from the working piston into a return chamber (24) with the exhaust valve.

Description

The invention relates to a device for simulating the recoil of a firearm, which is converted as a laser weapon for training purposes and has a movable between a closed starting position and an open end position and movable closure with a slide-off.

Laser weapons of the generic type are for example from the WO 98/14745 known. It describes a blowback system for weapons with built-in laser for the "sharpshooter simulation". A specially made mechanism is used to trigger the check system. However, this mechanism allows only a trigger resistance, which does not correspond to the actual conditions of the various types of weapons and is therefore perceived as inadequate in practice. In addition, the known check system requires either a complete new building or a conversion of known guns, which by design is extremely complex and therefore expensive, with an economic dismantling is not possible or largely excluded.

Furthermore, from the EP 1 262 728 A1 a laser gun and a method for converting a Scharfschusspistole to the laser gun known. In this construction, a compressed gas magazine is provided, which is adapted in terms of its dimensions to the magazine of each model to be converted the gun and connected via a connection valve with a magazine connector is. This magazine connecting piece has a through hole with an opening pin for the connection valve and a connection to the compressed gas magazine and a screw connection to an expansion chamber in the carriage above the running block. Furthermore, the firing pin is maintained in its position and operation after the model to be converted. The piston is disposed in the expansion chamber with a longitudinal bore and a reciprocating hammer in front of the plunger of the valve. Between the hammer and the piston inner wall a slight slippage or a slight clearance is provided for venting the expansion chamber. In this case, the spring rod is adapted with return spring to the prevailing pressure conditions to push back on the carriage, the piston and the hammer.

In this known laser gun, the mechanics of most available on the market guns should be preserved, so that the trigger weight or the pressure point of the original weapon is also maintained. Here is a relatively simple conversion or a simple conversion of previously known Scharfschusspistolen be made possible to pistols with a recoil simulation and laser triggering. The conversion is to require only the replacement of certain components, with a decommissioning in the original state should be easily possible.

In this construction, therefore, a gas pressure cartridge is used and a special valve control, which is triggered relatively expensive. It shows that due to the decreasing gas pressure in the gas pressure cartridge, the recoil simulation is weakened with increasing operating time. In addition, after consuming the gas pressure cartridge only a costly replacement or complex refilling possible. It has also been found that in such systems, which work with gas pressure cartridges for "recoil simulation", by the substantially abrupt expansion of the gas can cool the weapon. In particular, when used in automatic weapons with rapid firing has been shown that after delivery of several salvos, the weapon can even "freeze", so that the kickback system is put out of action. In addition, the compressed gas is discharged to the outside, which is also undesirable.

Accordingly, the invention has for its object to provide a device for simulating the recoil of a firearm, wherein in particular even with prolonged operating time or after delivery of multiple firing a freezing does not occur and also occur no emissions to the outside.

The object is achieved according to the invention together with the features of the preamble of claim 1, characterized in that a control mechanism for controlling a hydraulic working piston is provided which is directly or indirectly in operative connection with the closure of the firearm and that the working piston can be acted upon by a hydraulic medium and in a the closure from its initial position to its end position moving working position is adjustable and that a valve pressure lever is provided, which is deflected by an actuating movement of the slide valve and causes an opening of a pressure valve, whereby the working piston Hydraulkmedium can be fed under high system pressure and that Pressure valve with a hydraulic medium receiving the hydraulic chamber is in communication and that the hydraulic chamber has a movable separating piston, which gefgef the hydraulic chamber of a pressure causing the system pressure the first gas pressure chamber is separated and is acted upon by the compressed gas with system pressure and that the working piston indirectly or immediately at the end of its actuating movement closing the pressure valve and simultaneously or with a time delay the opening of a Exhaust valve causes and that the hydraulic medium is passed with open exhaust valve from the working piston in a return chamber.

Due to the inventive design, a device for recoil simulation of a firearm of any kind is provided, in which neither a "freezing" of the firearm - even with the delivery of sustained fire - may occur even an emission example of pressurized gas to the outside occurs.

For this purpose, a hydraulically-pneumatically combined pressure accumulator is provided for the admission of the working piston with hydraulic medium. The system pressure is set in a pneumatic gas pressure chamber filled with compressed gas. This gas pressure chamber is directly associated with a hydraulic chamber, wherein the hydraulic chamber and the gas pressure chamber are separated by an axially adjustable separating piston. Accordingly, this separating piston is acted upon by the pneumatic system pressure of the gas pressure chamber and transmits this system pressure to the hydraulic chamber by means of its axially displaceable and tight reception between the two chambers.

By means of a pressure valve which can be actuated by means of a control mechanism, this hydraulic system pressure can be supplied to the working piston temporarily, so that it can be adjusted abruptly from a stationary starting position, possibly counter to a spring force of a piston return spring, into a working position. This adjusting movement is transmitted to the closure of the firearm so that it moves from its closed starting position into its open end position. The opening of the pressure valve is effected by the adjusting movement of the gate valve, the adjusting movement, as is well known in firearms, for example, by a tee cock is effected. The dimensioning of the gas volume of the gas pressure chamber, the hydraulic volume of the hydraulic chamber and the working volume In addition to Stellwerg the working piston are coordinated so that several "shots" can be delivered without the system pressure noticeably weakens. This system pressure can be 400 bar and more and should not be less than 100 bar.

This control mechanism is further designed such that the opening of the exhaust valve at most simultaneously (but preferably delayed) takes place with the closing of the pressure valve. Thus, when the exhaust valve is opened, the working piston is depressurized. By opening the exhaust valve now the working piston can move back to its original position, which can be effected for example by an integrated piston return spring. The hydraulic medium in the working cylinder of the working piston is conveyed approximately "depressurized" via the outlet valve into a return chamber during this return movement of the working piston. This return chamber is thus filled gradually during the delivery of several "shots". In this case, an adjusting piston may be provided in the return chamber, which is received axially displaceable and tight to increase the volume of the return chamber in the return chamber. If the hydraulic volume of the hydraulic chamber is completely consumed, then the consumed hydraulic volume is thus completely in the return chamber and the actuating piston has accordingly reached a predetermined end position.

With appropriate design of the pressure valve and the exhaust valve - in the form of check valves - and the leadership of the associated connection channels, the entire hydraulic medium can be promoted back into the hydraulic chamber by resetting the control piston in the return chamber from its end position to its initial starting position. The device is again "charged" and ready to be dispensed the next "shotgun series" are used again in the firearm. By this "loading" by simply pushing back the actuator piston in the return chamber extremely short "load times" can be reached, so that the device can be kept ready for use on site without much effort for multiple applications.

Due to the design according to the invention, extremely high acceleration values of the closure can be achieved, so that a realistic recoil simulation can be achieved. Furthermore, in the device according to the invention a completely self-contained pressure system is used and no medium is released to the outside, so that this device is absolutely safe to use for recoil simulation.

Further advantageous embodiments can be found in the dependent claims.

Thus, it can be provided according to claim 2, that the control mechanism has a check lever, which is operatively connected to the closure and that the check lever for indirect control of the actuating movement of the closure and for the indirect control of the pressure valve and the outlet valve pivotally mounted in a control head of a housing and is rotatably driven by the working piston or a piston rod of the working piston. Due to this configuration of the control mechanism, the device can be used in particular for small-sized firearms. The kinetic energy of the working piston is transmitted through the check lever on the closure. The device can be inserted into the magazine holder of the firearm. That is, only the part to be inserted into the magazine holder is to be made small. The remaining housing of the device projects transversely out of the firearm, as is already known in cartridge magazines. In this inserted state, the check lever is in Housing of the firearm in the immediate vicinity of the lock. The stroke direction of the working piston can now also be directed transversely to the direction of adjustment of the closure, whereby it is also achieved that the housing can protrude transversely from the firearm. The transverse to the adjusting movement of the closure stroke movement is converted by the, preferably designed as an angle lever, check lever in a pivoting movement, which in turn, possibly with a predetermined transmission ratio, is transmitted to the closure.

In firearms with larger housings, the complete device can be used in the housing in the axial extension of the adjusting movement of the closure. In such cases, an indirect transfer of the kinetic energy of the working piston to the closure is not absolutely necessary, since the working piston can also be arranged in alignment with the closure. Thus, the shutter can also be directly driven directly by the working piston. The check lever is therefore not mandatory for every purpose.

It can further be provided according to claim 3, that the pressure valve has a plunger, via which a valve ball of the pressure valve from its closed position can be brought into its open position and that the plunger is adjustable by a finger follower whose adjusting movement by the valve pressure lever in the active , deflected working position is effected. Due to the provided drag lever transverse forces and consequent larger frictional forces are avoided or at least reduced so much that both the plunger and the valve pressure lever have the lowest possible degree of wear when depressing and relieving the plunger.

According to claim 4 it can be provided that the active, deflected working position of the valve pressure lever by a latching with the valve pressure lever engaged, with a blocking element provided catch lever is fixed and that the check lever has a Auslenknase which is engageable with a stop web of the catch lever in operative connection, that the catch lever is adjustable from its locking with the valve pressure engagement position in the end of the actuating movement of the check lever in a non-blocking the valve pressure lever position , By means of this embodiment, a sufficiently long opening time of the pressure valve is achieved, in particular when the outlet valve is closed, which essentially depends on the travel of the check lever and thus also of the working piston. This ensures that the working piston carries out its maximum possible adjusting movement. Since the check lever suspends the locking of the catch lever and thus of the valve pressure lever only in the end of his own adjusting movement, it is also ensured that the pressure valve remains open until reaching this travel and the working piston is pressurized with system pressure. Thus, the closure over the check lever against a spring resetting the closure spring force is safely driven to its predetermined end position.

Further, it can be provided according to claim 5, that a spring-loaded lever is provided, which is held by the locking element of the catch lever in an inactive starting position and that the catch lever can be brought by the Auslenknase after release of the valve pressure lever at the end of the actuating movement of the check lever in a switching position , in which the adjusting lever is released and that the adjusting lever executes an actuating movement after its release, by means of which a further lever element is adjustable into an active pivoting position for opening the outlet valve. This configuration ensures that the opening of the outlet valve takes place only immediately after the closing of the pressure valve, since the activation of the adjusting lever, which the exhaust valve via the lever element opens depends on the travel of the check lever. The check lever releases the catch lever provided for the locking of the catch lever in its inactive position only at most simultaneously with the closing operation of the pressure valve, so that a complete opening of the exhaust valve can be done safely only after the closing of the pressure valve. Thus, even a "flow" of standing under system pressure hydraulic medium directly from the hydraulic chamber in the return chamber is excluded, so that the pressure energy of the hydraulic medium is fully usable and is not lost in part by this type of "leakage".

Due to the embodiment according to claim 6 closing the exhaust valve is certainly only allowed when the working piston has reached its original starting position. For this purpose, it is provided that the active pivot position of the lever element is fixed by a resiliently engageable with the lever element in connection, provided with a locking finger locking lever and that the locking lever has a located in the blocking position of the locking lever in the movement path of the closure lever and that the locking lever can be brought by the return movement of the closure by an interaction of the closure with the deflection lever in a neutral, the lever element non-blocking position. Since the closure only shortly before reaching its original starting position, the locking effect of the locking lever repeals and only then the lever element to close the exhaust valve is released again, the exhaust valve can be closed only shortly before reaching the initial position of origin of the entire drive. Thus, the device for delivering a new "shot" for recoil simulation is safe just before reaching the starting position of the shutter (and thus the firearm itself) again "sharp". Due to this configuration, the device is not only for the delivery of "single shots" for Rebound simulation for sustained fire or for single shot volleys optimally suited.

The embodiment according to claim 7 ensures that the lever can not accidentally obstruct the opening of the exhaust valve, since it is "forced" by the check lever on its return to the starting position. For this purpose, it is provided that the non-return lever has a setting lever which can be brought into operative connection with a return lever of the adjusting lever and that the adjusting lever can be adjusted by the setting pin into its initial starting position via the return lever during the return movement of the non-return lever into its non-deflected initial position.

The design of the feature combinations of the subclaims taken alone or in different combinations with each other are for safe operation of the device according to the invention for recoil simulation of great advantage. However, in particular, the mechanical functional components, which are essentially designed like a lever here, can also be configured partially in the form of slider controls or the like. This is conceivable in particular when the working piston, with sufficient installation space, acts directly on the closure directly with a positioning force.

Fig. 1

eine perspektivische Darstellung eines Ausführungsbeispiels einer erfindungsgemäßen Vorrichtung mit einem Gehäuse sowie einem Steuerkopf, welcher eine Steuermechanik aufweist;

Fig. 2

einen Schnitt II - II der Vorrichtung aus Fig. 1 ohne Steuermechanik;

Fig. 3

einen vergrößerten Teilschnitt III - III des Steuerkopfes der Vorrichtung aus Fig. 1 durch den Arbeitskolben ebenfalls ohne Steuermechanik;

Fig. 4

einen kombinierten Horizontal- und Vertikalschnitt des Gehäuses der Vorrichtung aus Fig. 1 mit der Darstellung dreier zusätzlicher Gasdruckkammern sowie einem teilweisen Horizontalschnitt der ersten Gasdruckkammer und der Rücklaufkammer;

Fig. 5

einen Vertikalschnitt der Vorrichtung aus Fig. 1 zusammen mit einem Verschluss und eine Abschlagschieber in der Ausgangsstellung aller Bauteile;

Fig. 6

eine vergrößerte Schnittdarstellung des Steuerkopfes der Vorrichtung aus Fig. 5 nach Aktivierung des Abschlagschiebers und geöffnetem Druckventil;

Fig. 7

eine Schnittdarstellung der Steuerkopfes aus Fig. 6 mit einer Schnittführung im Bereich des Arbeitskolbens nach Aktivierung des Arbeitskolbens;

Fig. 8

die Schnittdarstellung aus Fig. 6 nach dem Schließen des Druckventils;

Fig. 9

die Schnittdarstellung aus Fig. 6 mit den mechanischen Bauteile zum Öffnen des Auslassventils unmittelbar vor deren Aktivierung;

Fig. 10

die Schnittdarstellung aus Fig. 9 in einer Funktionsstellung der Funktionsbauteile bei geöffnetem Auslassventil und geschlossenem Druckventil;

Fig. 11

die Schnittdarstellung aus Fig. 10 mit zurück gestelltem Rückschlaghebel und zurück gestelltem Stellhebel.

Reference to an embodiment, the invention is explained below in connection with the drawings. As already mentioned above, the drawing is used here only for a better understanding of the invention and its operation.

Fig. 1

a perspective view of an embodiment of a device according to the invention with a housing and a control head, which has a control mechanism;

Fig. 2

a section II - II of the device Fig. 1 without control mechanism;

Fig. 3

an enlarged partial section III - III of the control head of the device Fig. 1 by the working piston also without control mechanism;

Fig. 4

a combined horizontal and vertical section of the housing of the device Fig. 1 with the representation of three additional gas pressure chambers and a partial horizontal section of the first gas pressure chamber and the return chamber;

Fig. 5

a vertical section of the device Fig. 1 together with a closure and a gate valve in the starting position of all components;

Fig. 6

an enlarged sectional view of the control head of the device Fig. 5 after activation of the gate and open pressure valve;

Fig. 7

a sectional view of the control head Fig. 6 with a cutting guide in the region of the working piston after activation of the working piston;

Fig. 8

the sectional view Fig. 6 after closing the pressure valve;

Fig. 9

the sectional view Fig. 6 with the mechanical components for opening the exhaust valve immediately before it is activated;

Fig. 10

the sectional view Fig. 9 in a functional position of the functional components with the exhaust valve open and the pressure valve closed;

Fig. 11

the sectional view Fig. 10 with set back lever and set back lever.

Fig. 1 shows a perspective view of an embodiment of a device according to the invention, which has a housing 2 in the present embodiment. In the upper end region of this housing 2 forms a control head 3, which forms two mutually parallel and spaced-apart bearing walls 4 and 5 at the top. Between these bearing walls, a control mechanism 6 is received, which in particular has a pivotally mounted check lever 7 in the present embodiment. In Fig. 1 while the check lever 7 is shown in its disengaged active working position. This check lever 7 is used for the sudden adjustment of a closure head of a firearm, as will be explained in more detail later. In this case, this check lever 7 is deflected by a hydraulically actuated working piston.

Furthermore, in Fig. 1 partly even a catch lever 8, a locking lever 9, a spring bearing 10 and a valve pressure lever 11 can be seen, their operation together with even more in Fig. 1 invisible mechanical components for controlling the actuating movement of the check lever 7 serve. Between the rigidly arranged on the bearing wall 5 spring bearing 10 and the locking lever 9 on the one hand and the spring bearing 10 and the catch lever 8 on the other hand each Axialdruckfedern may be provided which cause corresponding control movements of the locking lever 9 and the catch lever 8 in certain operating situations. The other hereinafter described in more detail lever parts can be provided to perform their respective adjusting or restoring movement in the region of their bearing axes each with a kind of leg spring, which are not shown in the drawing, as known from the prior art.

Fig. 2 shows a partial section II - II Fig. 1 of the housing 2 without the control mechanism 3 arranged in the control head 6 Fig. 1 ,

In Fig. 2 is in the region of the rear bearing wall 4, a piston rod 12 recognizable, which is part of the above-mentioned working piston and in Fig. 3 is identified by the reference numeral 34. Furthermore, it is off Fig. 2 It can be seen that a hydraulic chamber 13 is provided in the housing 2, in the lower region of which a separating piston 14 is received so as to be axially adjustable in the direction of the double arrow 15. The separating piston 14 is sealingly inserted in the hydraulic chamber 13 with a ring seal 16. It is off Fig. 2 recognizable that the hydraulic chamber 13 below the separating piston 14 forms a first gas pressure chamber 17, which is sealed on the underside by means of a screw plug 18. From the hydraulic chamber 13, a pressure channel 19 leads to a pressure valve 20, which is arranged fixed in the control head 3. This pressure valve 20 has a valve ball 21, which is actuated via a plunger 22 for opening the pressure valve 20. D. h., That upon actuation of the plunger 22, the valve ball 21 is moved in the direction of arrow 23 and thus the pressure valve 20 is opened. The hydraulic chamber 13 takes on a liquid hydraulic medium, which when opening the pressure valve 20 for activating the working piston 34 from Fig. 3 and thus the piston rod 12 to the working piston 34 can be fed. The piston rod 12 moves from pressurizing the working piston 34 of FIG Fig. 2 shown in solid lines starting position in the direction of arrow 38 in the in Fig. 2 in the dashed lines shown end position.

The hydraulic chamber 13 adjacent to a downwardly open return chamber 24 is assigned, in which an actuating piston 25 is arranged adjustable in the direction of the double arrow 15. Also the actuating piston 25 is received via annular seals 26 axially adjustable sealing in the return chamber 24. Above the return chamber 24, an outlet valve 30 is provided which also has a valve ball 31. This valve ball 31 is actuated via a second plunger 32 and serves to relieve the pressure of the working piston 34 Fig. 3 That is, after the closing of the pressure-side pressure valve 20, the outlet valve 30 is opened and thus during a return movement of the piston rod 12 together with the working piston 34 from Fig. 3 Hydraulic medium passes through the outlet valve 30 in the return chamber 24. During this return flow of the hydraulic medium, the adjusting piston 25 moves in the direction of the arrow 23 downwards. Next is out Fig. 2 a horizontally extending connecting channel 41 hinted recognizable, which inter alia a cylinder 36 of the working piston 34 from Fig. 3 with a return passage 43 of the exhaust valve 30 connects.

It is thus easy to imagine that by alternately opening the pressure valve 20 and the outlet valve 30 to the working rod connected to the piston rod 12 34 from Fig. 3 Hydraulic medium can be supplied and during the return movement of the working piston hydraulic fluid can be discharged. By appropriate control thus performs the piston rod 12 of the working piston an alternating movement in the direction of the double arrow 15, whereby the spring-loaded check lever 7 a corresponding alternating or oscillating pivotal movement in the direction of the double arrow 33 (FIGS. Fig. 1 ) for moving a locking head of a firearm.

Fig. 3 shows a perspective enlarged partial section of the upper end portion of the housing 2 together with the control head 3. In Fig. 3 the control mechanism 6 is also not shown for the sake of clarity. It can be seen that in a central, vertically oriented cylinder 36 a Cylinder sleeve 35 is inserted. This cylinder liner 35 has a stepped bore 37 in the axial direction, in the upper, tapered portion of the piston rod 12 is mounted without play. In the radially enlarged region of this through hole 37, the actual working piston 34 adjoins this piston rod 12. In this case, there is this working piston 34 in the in Fig. 3 shown position in its deflected in the direction of arrow 38 working position. In its neutral starting position of the working piston 34 is moved together with the piston rod 12 in the direction of arrow 23 vertically downwards, as indicated by the dashed lines 39 in Fig. 3 is recognizable.

Furthermore, it is off Fig. 3 a laterally arranged next to the working piston 34 pressure channel 40 can be seen, which communicates with its lower end portion via the connecting channel 41 with the cylinder 36 in connection. Approximately equal to the dashed lines 39 of the working piston 34, a transverse bore 42 is provided, which in the present embodiment from the plane to the in Fig. 3 invisible pressure valve 20 leads. D. h., That when opening the pressure valve 20 off Fig. 2 via the transverse bore 42, the pressure channel 40 and the connecting channel 41 of the cylinder 36 can be acted upon by system pressure hydraulic fluid, so that the working piston 34 from its in Fig. 3 in dashed lines 39 shown starting positions is adjusted in the end position shown in solid lines. If the pressure in the cylinder 36 is reduced again, the working piston 34 in turn moves back into the starting position 39 shown in dashed lines 39, which is brought about by a restoring spring, not shown in the drawing, of the working piston 34.

In this case, in this return movement in the direction of arrow 23, the pressure valve 20 is closed again. That's in the cylinder 36 located below the working piston 34 hydraulic medium in the in Fig. 2 In this case, the connecting channel 41 is formed extended in the horizontal direction and leads from the cylinder 36 into a first return channel 43 below the outlet valve 30 (FIG. Fig. 2 ). This outlet valve 30 in turn is in turn connected to a second return channel (in Fig. 2 not visible) in connection with the return chamber 24, so that hydraulic medium can pass through these channels into the return chamber 24. In this case, the adjusting piston 25 moves in the return chamber 24 in the direction of arrow 23 vertically downwards, whereby the volume of the return chamber 24 is increased by a corresponding volume.

That is, due to this special activation of the pressure valve 20 and the outlet valve 30, the working piston 34, together with its piston rod 12, carries out an alternating adjusting movement in the direction of the double arrow 15. This in turn causes an alternating pivoting movement of the check lever 7 in the in Fig. 1 illustrated direction of the double arrow 33rd

To pressurize the first gas pressure chamber 17 with the required system pressure, a plurality of gas pressure chambers 50, 51 and 52 are provided in the present embodiment in the housing 2, as shown in the perspective, combined horizontal and vertical sectional view of Fig. 4 is recognizable. It is off Fig. 4 can be seen that these gas pressure chambers 50, 51 and 52 are arranged parallel to the partially visible gas pressure chamber 17 with its screw plug 18 and the return chamber 24 extending in the housing 2. In this case, the gas pressure chambers 50 and 51 communicate with each other via a corresponding slot connection 53 in their lower end region, so that pressurized gas corresponding to the gas pressure chamber 50 can "flow in" into the pressure chamber 51. Furthermore the two gas pressure chambers 51 and 52 via a respective slot connection 54 and 55 with the first gas pressure chamber 17 in conjunction, so that corresponding gas at an upward movement of the separating piston 14 (FIG. Fig. 2 ) can flow in the direction of arrow 38 in the first gas pressure chamber 17.

Due to the provided gas pressure chambers 50, 51 and 52 thus the system pressure in the hydraulic chamber 13 causing gas pressure is reduced only insignificantly after a stepwise executed adjusting movement of the separating piston 14 in the direction of the arrow 38, so that in particular the working piston 34 in its upward movement in the direction of the arrow 38 ( Fig. 3 ) is acted upon at least approximately the same system pressure over the entire working stroke of the separating piston 14. Accordingly, the actuating forces on the piston rod 12 during the upward movement in the direction of the arrow 38 at each stroke are approximately constant. That's how it turns out Fig. 1 apparent check lever 7 is driven with a correspondingly constant torque in the direction of arrow 56.

For filling the first gas pressure chamber 17 and the communicating with this, further gas pressure chambers 50 to 52, for example, the screw plug 18 may be provided with a corresponding pressure port.

The filling of the hydraulic chamber 13 with hydraulic medium, for example, via the in Fig. 3 shown pressure channel 40 made, which is closed on the upper side with a corresponding screw 44. The filling of the system with hydraulic medium is preferably carried out in the pressureless state, so that the screw plug 44 does not have to have any pressure connection, but is only to remove for filling.

In the following drawing figures, the operation of the invention is explained in more detail by way of example.

So shows Fig. 5 a vertical section through the housing 2 with its control head 3, wherein the cutting plane is guided approximately centrally by the hydraulic chamber 13 and the first gas pressure chamber 17. In this case, the housing 2 in the region of this hydraulic chamber 13 and the gas pressure chamber 17 is shown shortened axially.

The inventive device 1 is designed in the present embodiment such that it (not shown in detail) can be inserted into the magazine holder of a firearm. In this area, such a weapon has a so-called. Lock 60, which is movable in the direction of the double arrow 61 back and forth. In the case of a conventional "sharp" weapon, this closure is abruptly moved counter to a spring force in the direction of the arrow 62 due to the gas pressure of the cartridge after the firing of the shot. To trigger a shot serves a so-called. Slam gate 63 which abruptly by a non-illustrated in the drawing tee cock in the direction of the arrow 64 is movable. At the end of its actuating movement, the slide-off slide 63 triggers the fuse of an inserted cartridge and thus a shot.

Since now the normally existing magazine is replaced by the device 1 according to the invention, therefore, no shot can be triggered, so that no bewirkter from the cartridge gas pressure can move the shutter 60 to the right in the direction of arrow 62. Accordingly, there is also a lack of the normally present "kickback", which, however, is simulated by the device 1 according to the invention.

For this purpose, the check lever 7 is in the in Fig. 5 illustrated retracted starting position in the trajectory of the shutter 60. Furthermore, it can be seen that the Valve pressure lever 11 is located in the path of movement of the slide valve 63. This valve pressure lever 11 is pivotally mounted in the bearing walls 4 and 5 via a bearing axis 65. In this case, the valve pressure lever 11 forms on the underside a disengaging element 66 which is mechanically connected to a drag lever 67 in operative connection. This drag lever 67 is also pivotally mounted in the bearing walls 4 and 5 via a corresponding bearing axis 68.

The valve pressure lever 11 forms a deflection lever 69 which extends in the in Fig. 5 shown starting position in the immediate vicinity of a deflection surface 70 of the slide valve 63 is located. If now the impact slide 63 is abruptly moved in the direction of the arrow 64, the valve pressure lever 11 is pivoted about the bearing axis 65 in the direction of the arrow 71 by the mechanical operative connection between the deflection surface 70 and the deflection lever 69. This in turn causes a substantially vertically downward in the direction of arrow 23 of the release element 66, whereby the drag lever 67 is also adjusted in the direction of arrow 23 down. This adjusting movement is then transmitted to the plunger 22 of the pressure valve 20, so that the valve ball 21 is lifted from its valve seat in the direction of the arrow 23. Accordingly, hydraulic medium, which is received under high system pressure in the hydraulic chamber 13, pass into a circumferential annular chamber 72 of the pressure valve 20. This annular chamber 72 is connected to a not further recognizable in the drawing, but in Fig. 3 indicated transverse bore 42 in operative connection. Accordingly, the pressurized hydraulic medium is already closed Fig. 3 mentioned, via this transverse bore 42, the pressure channel 40 and the connecting channel 41 to the cylinder 36 of the working piston 34 Fig. 3 fed.

The end position of the slide-off slide 63 and the valve pressure lever 11 is off Fig. 6 seen. It is also recognizable that the drag lever 67 is pressed by the release element 66 of the valve pressure lever 11 in the direction of the arrow 23 vertically downwards. Accordingly, the plunger 22 is adjusted in the same direction, so that the valve ball 21 is in a raised, vertically downwardly adjusted position relative to its valve seat 73. In Fig. 6 is behind the drag lever 67, the piston rod 12 of the not recognizable working piston 34 visible. Also is off Fig. 6 the annular chamber 72 of the pressure valve 20 open into which transverse bores 27 of the pressure valve 20 open.

Since now the working piston 34 ( Fig. 3 ) is subjected to system pressure, the check lever 7 is deflected in the direction of arrow 56 by the piston rod 12 rotating. He comes with the shutter 60 into contact, so that it is abruptly adjusted by this adjusting movement of the check lever 7 in the direction of arrow 62. In this deflected position of the valve pressure lever 11, this is secured by the catch lever 8, which engages a corresponding locking lug 74 with a locking element 75. In this case, the catch lever 8 is held by spring force in this locking position. This blocking position is defined by a radially directed to the bearing axis 76 of the catch lever 8 vertically downward stop ridge 77. By blocking the valve pressure lever 11 in the in Fig. 6 shown position is thus ensured that the pressure valve 20 remains open at least over a certain time, so that the working piston 34 (FIG. Fig. 3 ) with its piston rod 12 can perform a complete stroke for deflecting or pivoting of the check lever 7 in the direction of the arrow 56.

Fig. 7 shows a sectional view of the housing 2 together with the control head 3, the cutting guide is approximately in the plane of the cylinder 39. It is in Fig. 7 the cylinder liner 35 in the partial cut recognizable and the piston rod 12. It can be seen that the piston rod 12 is in its "extended" working position. The check lever 7 has been adjusted in the direction of the arrow 56 and accordingly the shutter 60 in the direction of the arrow 62. In Fig. 7 are the other elements of the control mechanism for the sake of clarity not shown. The check lever 7 forms in the vicinity of its bearing axis 65 a radial to this bearing axis 65 extending actuator 78, which is in operative connection with the piston rod 12. This adjusting element 78 has, together with the piston rod 12, a relatively small radial distance to the bearing axis 65, while the non-return lever 7 has a relatively large radial distance from the bearing axis 65 with its upper striking element 79. By means of these different "lever lengths", an extremely high ratio is achieved, so that the closure 60 can also be accelerated sufficiently in the direction of the arrow 62 by the striking element 79.

Furthermore, a deflection nose 80 is provided on the check lever 7 substantially diametrically opposite the actuating element 78, said deflection lug being provided with the stop ridge 77 of the catch lever 8 (FIG. Fig. 6 ) can be brought into operative connection. This active compound shows Fig. 8 on average. It can be seen that by the adjusting movement of the check lever 7 this stop lug 80 slides along the inside of the stop web 77 and thus this stop web 77 is moved together with the entire catch lever 8 in the direction of the arrow 81 against a spring force. Thus, the catch lever 8 comes with its locking element 75 with the locking lug 74 of the valve pressure lever 11 disengaged, so that the valve pressure lever 11 can move back in the direction of arrow 82 back to its starting position. This return movement is also effected by spring force.

Furthermore, so that the drag lever 67 is relieved and moves in the direction of arrow 38 vertically upwards, so that the plunger 22 of the pressure valve 20 is released. This in turn closes the valve ball 21, since it returns to its valve seat 73 by acting in the pressure channel 19 system pressure. Thus, now the cylinder 36 of the working piston 34 ( Fig. 3 ) separated from the hydraulic chamber 13, so that no hydraulic medium more "nachströme" can. However, this subsequent flow of hydraulic medium is also limited by the limited adjusting movement of the working piston 34, since the working piston 34 is radially offset relative to its piston rod 12, as is made Fig. 3 is apparent. After closing the pressure valve 20, the working piston 34 can now be relieved again.

This is done by a further adjusting movement of the check lever 7. This further adjusting movement is thereby Fig. 9 to be taken in section. Behind the in Fig. 9 Not shown valve pressure lever 11 is another lever 83, which in the in Fig. 8 shown position of the catch lever 8 by the blocking element 75 in a starting position (shown in phantom) is fixed. The adjusting lever 83 is also rotatably mounted on the bearing shaft 65 of the valve pressure lever 11. By a leg spring or the like., The adjusting lever 83 is acted upon in the direction of arrow 82 with a spring force. Now, the check lever 7 in the in Fig. 9 shown position in the direction of the arrow 56, so the catch lever 8 is rotated on the Auslenknase 80 and its stop web 77 further in the direction of the arrow 81, so that the blocking element 75 of the catch lever 8 moves vertically downward in the direction of arrow 23 and thus a locking lug 84 of the actuating lever 83 is released. By this release, in turn, a lever member 85, which on the bearing axis 68 of the Towing lever 67 is rotatably mounted, offset in a rotational movement in the direction of arrow 86.

This rotational movement of the lever member 85 is effected by the adjusting lever 83. For this purpose, this adjusting lever 83 has a sliding element 87 directed towards the lever element 85, which is in operative connection with an actuating element 88 of the lever element 85. Next is out Fig. 9 recognizable that the lever member 85 is disposed above the plunger 32 of the exhaust valve 30. Accordingly, the lever member 85 performs a rotational movement in the direction of arrow 86, the lever member 85 moves with its outer end in the direction of arrow 23 vertically downwards. This in turn causes an actuating movement of the plunger 32 in the same direction, so that the valve ball 31 of the exhaust valve 30 is also moved in the same direction. Thus, this valve ball 31 lifts off from the valve seat 90 of the exhaust valve 30, so that the exhaust valve 30 is opened.

About a suitably ausgestaltetes channel system, in particular via the cylinder 60 and in Fig. 9 Thus, recognizable connecting channel 41 can thus flow back hydraulic medium through the outlet valve 30. This outlet valve 30 also forms a circumferential annular channel 91, which opens into an outlet channel 92. This outlet channel 92 is in turn connected to the in Fig. 5 dashed return channel 93 in conjunction. Thus, the hydraulic medium enters the open outlet valve 30 in the Fig. 5 This return flow of the hydraulic medium in the return chamber 24 whose adjusting piston 25 is adjusted vertically in the direction of arrow 23, so that the cylinder 36 of the working piston 34 is completely depressurized. This piston 34 is thus by spring force (in the drawing, the compression spring is not shown) back into his in Fig. 3 Dashed position shown starting position 39 adjustable.

This open position of the exhaust valve 30 is in Fig. 10 shown. It can be seen that the lever member 85 has been adjusted by its actuator 88 on the ramp surface 87 of the actuating lever 83 in its the plunger 32 depressing end position. The valve ball 31 is lifted off the valve seat 90. By corresponding transverse bores 94 hydraulic medium now passes from the connecting channel 41 via the transverse bores 94 in the annular channel 91 of the outlet valve 30 and from there via the also in Fig. 5 illustrated outlet passage 92 and the return passage 93 in the return passage 24. In this case, the lever member 85 by a locking lever 95 in its adjusted working position of the Fig. 10 held. This in Fig. 10 located in front of the catch lever 8 locking lever 95 is in Fig. 10 shown in dashed lines and rotatably supported on a common axis of rotation 100 together with the catch lever 8. In this case, the control lever 85 enters due to a spring force in the Fig. 10 illustrated blocking position.

Due to the fact that now the exhaust valve 30 is opened, from the cylinder 36 of the working piston 34 hydraulic medium via the connecting channel 41 through the outlet valve 30 through or through the transverse bore 94, the outlet channel 92 and the associated with this return channel 93 back in enter the return chamber 24. Thus, the working piston 34 is off Fig. 3 depressurized, so he out of the Fig. 3 shown in solid lines working position is moved back into the neutral position shown in dashed lines 39 by spring force. At the same time the check lever 7 moves against the arrow 56 back to its original position. On the check lever 7, a transverse adjusting pin 102 is provided in the region of its Auslenknase 80, by which during the return movement of the check lever 7 against the arrow 56 of the lever 83 is reset against the arrow 82 in its initial position. For this purpose, the Lever 83 to a reset lever 103, which comes during the return movement of the check lever 7 with the actuating pin 102 in operative connection.

The deferred position is in Fig. 11 shown. It can be seen that the adjusting pin 102 is in engagement with the return lever 103 and the adjusting lever 83 is thus held in its initial position. Furthermore, from the Fig. 10 and 11 also recognizable that the exhaust valve 30 is also still open. This is due to the blocking effect of the locking lever 95 with its locking finger 96.

Next is out Fig. 11 it can be seen that this locking lever 95 has the locking finger 96 approximately diametrically opposite a vertically over the two bearing walls 4 and 5 also protruding lever 97.

Now moves the shutter 60 in the direction of the arrow 64, so it comes with the lever 97 in operative connection.

Now moves the shutter 60 off Fig. 10 together with the slide valve 63 back in the direction of the arrow 64, the locking lever 95 is moved back by the shutter 60 in the direction of the arrow 101, so that the lever member 85 is released in turn. Previously, however, it is necessary that the check lever 7 against the arrow 56 returns to its original position. This is also done automatically by spring force as soon as the piston rod 12 out Fig. 10 again in the direction of arrow 23 in their initial position (s. Fig. 3 ) has moved back.

After the return movement of the shutter 60 in the in Fig. 5 shown starting position, the control mechanism 6 is also fully restored to its original position. By re-activating the slide valve 63 can now the next "shot" will be effected. The same processes always take place, as described above for the drawings 5 to 11.

The invention is not limited to the illustrated control mechanism 6. It is essential in the invention that can be accelerated abruptly in the direction of arrow 62 by a combination of gas pressure chambers and a hydraulic chamber and a working piston and the special valve control of the shutter. Due to the special design of the control mechanism, the pressure valve and the outlet valve are actuated sequentially, wherein in the illustrated embodiment, this operation is also dependent on the adjusting movement of the check lever. This adjusting movement of the check lever causes on the one hand the opening and closing of the pressure valve 20 and on the other hand also the opening of the outlet valve 30. By the return movement of the shutter 60, this outlet valve 30, as described above, closed again, so that the system returns to its original state ,

By firing several firing sequences of the separating piston 14 ( Fig. 5 ) is successively or stepwise in the direction of arrow 38 in the hydraulic chamber 13 moves upward. After a certain number of "shots", which depends on the volume ratio of the hydraulic chamber 13, the piston stroke and piston cross section of the working piston 34, the separating piston 14 reaches an upper end position. At the same time, the actuating piston 25 in the return chamber 24 moves stepwise in the direction of the arrow 23 (FIG. Fig. 5 ) down until it also reaches an end position.

After reaching the two end positions of both the separating piston 14 and the actuating piston 25, the device 1 can now be "charged" again by simply (under possibly high expenditure of force) the actuating piston 25 again in the direction of Arrow 38 is pressed. The hydraulic medium located in the return chamber 24 is then pushed through the return passage 93, the outlet channel 92, the annular channel 91 and the transverse bores 94 through the outlet valve 30. The opening of the outlet valve 30 takes place automatically, since this "overpressure" the valve ball 31 inevitably lifts from its valve seat 90. After passing through the hydraulic medium through the outlet valve 30, this passes through the connecting channel 41 (FIG. Fig. 3 . 10 and 11 ), the pressure channel 40 and the transverse bore 42 into the annular chamber 72 of the pressure valve 20. Due to the overpressure, the hydraulic medium is now forced through the cross bores 27 also present the pressure valve 20 into the pressure valve 20. As a result, an adjusting movement of the valve ball 21 in the direction of the arrow 23 is effected, so that this pressure valve 20 is also opened. About the in Fig. 6 By way of this "pushing back" of the hydraulic medium into the hydraulic chamber 13, the separating piston 14 is thus in turn inevitably moved in the direction of the arrow 23 (FIG. Fig. 5 ) pressed down until it has reached its original starting position again.

An extremely advantageous feature of this construction is that the device according to the invention has a closed hydraulic circuit and does not deliver any compressed gas to the outside during operation. D. h., That the device 1 on the one hand in advance is first to fill with hydraulic medium and then corresponding compressed gas is filled into the gas pressure chambers 50, 51 and 52 and in the first gas pressure chamber 17 under high pressure. After the "filling" of the device according to the invention, this is thus ready for use.

At this point, it should be noted that, in particular, the drive of the closure 60 effected via the check lever 7 is not must necessarily be designed in this way. The described embodiment relates to smaller firearms, in which only a small installation space for such a device 1 is present. In this case, the housing 2 of the device 1 with its control head 3 is designed such that the control head 3 can be inserted into the magazine shaft of the corresponding firearm, so that the non-return lever 7 is in the region of the movement path of the closure 60. For larger firearms, especially with a larger housing, it is also conceivable that the shutter 60 is driven directly by the piston rod 12 of the working piston 34. Accordingly, then the control mechanism 6 is adapted to accomplish the above-described valve control of the pressure valve 20 and the exhaust valve 30 can.

Also, of course, other control mechanisms with differently designed "control levers" are conceivable, which ensure the same purpose or the same operation as described in the embodiment. Instead of such "pivoting lever", as these are used in the control mechanism 6, also slider controls and the like. More are conceivable.

Claims (7)

Device (1) for simulating the recoil of a firearm, which is converted as a laser weapon for training purposes and has a closure (60) which can be moved back and forth between a closed starting position and an open end position, with a knock-off slide (63), characterized
that a control mechanism (6) for controlling a hydraulic working piston (34) is provided, which with the closure (60) of the firearm is directly or indirectly in operative connection and,
in that the working piston (34) can be acted on by a hydraulic medium and is adjustable in a working position which moves the closure (60) from its starting position into its end position, and
that a valve push lever (11) is provided which can be deflected by an adjusting movement of the tee slide (63) and an opening of a pressure valve (20) effected, whereby (34) Hydraulkmedium be supplied to the working piston under high system pressure and,
that the pressure valve (20) with a hydraulic medium receiving hydraulic chamber (13) is connected and,
that the hydraulic chamber (13) comprising a movable separating piston (14), said hydraulic chamber (13) sealed by a filled with a system pressure causing pressurized gas first gas pressure chamber (17) separates and is acted upon by the compressed gas with a system pressure and,
in that the working piston (34), directly or indirectly at the end of its adjusting movement, causes the closing of the pressure valve (20) and, simultaneously or with a time delay, the opening of an outlet valve (30), and
that the hydraulic medium is passed from the working piston (34) into a return chamber (24) when the outlet valve (30) is open. Apparatus according to claim 1, characterized in that the control mechanism (6) comprises a check lever (7) which is in operative connection with the closure (60) and,
in that the check lever (7) is pivotably mounted in a control head (3) of a housing (2) for indirect control of the actuating movement of the closure (60) and for the indirect control of the pressure valve (20) and the outlet valve (30) and actuated by the working piston (34 ) or a piston rod (12) of the working piston (34) is rotationally driven. Apparatus according to claim 1 or 2, characterized in that the pressure valve (20) has a plunger (22), via which a valve ball (21) of the pressure valve (20) can be brought from its closed position into its open position and,
that the plunger (22) by a drag lever (67) is adjustable, the adjusting movement is effected by the valve pressure lever (11) in its active, deflected working position. Apparatus according to claim 3, characterized in that the active, deflected working position of the valve pressure lever (11) by a with the valve pressure lever (11) latching engaged, with a locking element (75) provided catch lever (8) is fixed and,
in that the catch lever (8) has a deflection nose (80) which can be brought into operative connection with a stop web (77) of the catch lever (8) in such a way that the catch lever (8) opens out of its engagement position in the end area of the catch valve engaging with the valve pressure lever (11) Adjustment movement of the check lever (7) in a the valve pressure lever (11) non-locking position is adjustable. Apparatus according to claim 4, characterized in that a spring-loaded adjusting lever (83) is provided, which by the blocking element (75) of the catch lever (8) in an inactive Home position is held and,
that the catch lever (8) can be brought into a switching position by the deflection nose (80) after release of the valve pressure lever (11) at the end of the adjusting movement of the check lever (7), in which the adjusting lever (83) is released and,
that the adjusting lever (83) executes an actuating movement after its release, by means of which a further lever element (85) is adjustable into an active pivoting position for opening the outlet valve (30). Apparatus according to claim 5, characterized in that the active pivotal position of the lever element (85) by a resiliently with the lever member (85) latchingly engageable, provided with a locking finger (96) locking lever (95) is fixed and,
the blocking lever (95) has a deflection lever (97) located in the blocking position of the blocking lever (95) in the path of movement of the closure, and
in that the locking lever (95) can be brought into a neutral position which does not block the lever element (85) by the return movement of the closure (60) through an interaction of the closure (60) with the deflection lever (97). Apparatus according to claim 6, characterized in that the non-return lever (7) has a with a reset lever (103) of the actuating lever (83) engageable actuating pin (102) and,
that the adjusting lever (83) is adjustable via the return lever (103) during the return movement of the check lever (7) in its non-deflected initial position by the adjusting pin (102) in its initial starting position.

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