EP2385337B1 - Système de recul pour armes à feu - Google Patents

Système de recul pour armes à feu Download PDF

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Publication number
EP2385337B1
EP2385337B1 EP10016002.7A EP10016002A EP2385337B1 EP 2385337 B1 EP2385337 B1 EP 2385337B1 EP 10016002 A EP10016002 A EP 10016002A EP 2385337 B1 EP2385337 B1 EP 2385337B1
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EP
European Patent Office
Prior art keywords
lever
valve
pressure
adjusting
piston
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EP10016002.7A
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German (de)
English (en)
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EP2385337A2 (fr
EP2385337A3 (fr
Inventor
Willi Rauser
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Individual
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Individual
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Publication of EP2385337A3 publication Critical patent/EP2385337A3/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F41—WEAPONS
    • F41A—FUNCTIONAL FEATURES OR DETAILS COMMON TO BOTH SMALLARMS AND ORDNANCE, e.g. CANNONS; MOUNTINGS FOR SMALLARMS OR ORDNANCE
    • F41A33/00—Adaptations for training; Gun simulators
    • F41A33/06—Recoil simulators

Definitions

  • 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 between a closed starting position and an open end position back and forth movable shutter with a slide-off.
  • a device according to the preamble of claim 1 is known from US 2006/0027225 known.
  • 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.
  • 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.
  • 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.
  • the spring rod is adapted with return spring to the prevailing pressure conditions to push back on the carriage, the piston and the hammer.
  • 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.
  • 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 characterized in that a valve pressure lever is provided, which is deflectable by an adjusting movement of the slide valve and causes an opening of a pressure valve, whereby the working piston Hydraulkmedium can be supplied under high system pressure and that the pressure valve is in communication with a hydraulic chamber receiving the hydraulic chamber, and in that the hydraulic chamber has a movable separating piston sealing the hydraulic chamber from one with a system pressure kenden compressed gas filled first gas pressure chamber and is acted upon by the pressurized 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
  • a device for recoil simulation of a firearm of any kind 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.
  • a hydraulically-pneumatically combined pressure accumulator 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.
  • 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.
  • the working piston is depressurized.
  • 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".
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the complete device can be used in the housing in the axial extension of the adjusting movement of the closure.
  • 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.
  • the shutter can also be directly driven directly by the working piston.
  • the check lever is therefore not mandatory for every purpose.
  • 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 drag lever whose adjusting movement through 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.
  • 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 ,
  • 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.
  • 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.
  • 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.
  • 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".
  • closing the exhaust valve is certainly only allowed when the working piston has reached its original starting position.
  • 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.
  • 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.
  • 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.
  • 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.
  • a control head 3 which forms two mutually parallel and spaced-apart bearing walls 4 and 5 at the top.
  • a control mechanism 6 is received, which in particular has a pivotally mounted check lever 7 in the present embodiment.
  • 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.
  • 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.
  • 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 ,
  • 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.
  • 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 to activate 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.
  • 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.
  • Fig. 3 shows a perspective enlarged partial section of the upper end portion of the housing 2 together with the control head 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.
  • the actual working piston 34 adjoins this piston rod 12.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a weapon has a so-called.
  • Lock 60 which is movable in the direction of the double arrow 61 back and forth.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • Fig. 9 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.
  • This rotational movement of the lever member 85 is effected by the adjusting lever 83.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 ,
  • the device 1 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.
  • this 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • control levers with differently designed “control levers” are conceivable, which ensure the same purpose or the same operation as described in the embodiment.
  • control levers instead of such "pivoting lever”, as these are used in the control mechanism 6, also slider controls and the like. More are conceivable.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
  • Aiming, Guidance, Guns With A Light Source, Armor, Camouflage, And Targets (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Claims (7)

  1. Dispositif (1) de simulation du recul d'une arme à feu, laquelle est transformée en arme à laser à des fins d'entraînement et possède une culasse (60) munie d'un curseur de détachage (63) qui peut effectuer un mouvement de va-et-vient entre une position initiale fermée et une position finale ouverte,
    un mécanisme de commande (6) étant prévu pour commander un piston de travail hydraulique (34), lequel est en liaison active directement ou indirectement avec la culasse (60) de l'arme à feu, et
    le piston de travail (34) pouvant être chargé par un fluide hydraulique et pouvant être amené dans une position de travail qui déplace la culasse (60) de sa position initiale dans sa position finale,
    caractérisé en ce
    qu'il est prévu un levier de pression de soupape (11) qui peut être dévié par un mouvement de réglage du curseur de détachage (63) et provoque une ouverture d'une soupape de pression (20), ce qui permet d'acheminer au piston de travail (34) du fluide hydraulique sous haute pression système, et
    en ce que la soupape de pression (20) est en liaison avec une chambre hydraulique (13) qui accueille le fluide hydraulique, et
    en ce que la chambre hydraulique (13) présente un piston de séparation (14) mobile, lequel sépare hermétiquement la chambre hydraulique (13) d'une première chambre pressurisée à gaz (17) remplie d'un gaz comprimé produisant la pression système et lequel est soumis à la pression système par le gaz comprimé, et
    en ce que le piston de travail (34) provoque directement ou indirectement à la fin de son mouvement de réglage la fermeture de la soupape de pression (20) et, simultanément ou avec un retard, l'ouverture d'une soupape de sortie (30), et
    en ce que lorsque la soupape de sortie (30) est ouverte, le fluide hydraulique est amené par le piston de travail (34) dans une chambre de retour (24).
  2. Dispositif selon la revendication 1, caractérisé en ce que le mécanisme de commande (6) présente un levier de retour (7) qui se trouve en liaison active avec la culasse (60), et
    en ce que le levier de retour (7), en vue de la commande indirecte du mouvement de réglage de la culasse (60) ainsi que de la commande indirecte de la soupape de pression (20) et de la soupape de sortie (30), est monté pivotant dans une tête de commande (3) d'un boîtier (2) et peut être entraîné en rotation par le piston de travail (34) ou par une bielle (12) du piston de travail (34).
  3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que la soupape de pression (20) présente un poussoir (22) par le biais duquel une bille de soupape (21) de la soupape de pression (20) peut être amenée de sa position fermée dans sa position ouverte, et
    en ce que le poussoir (22) peut être amené par un levier entraîneur (67) dont le mouvement de réglage est produit par le levier de pression de soupape (11) dans sa position de travail active déviée.
  4. Dispositif selon la revendication 3, caractérisé en ce que la position de travail active déviée du levier de pression de soupape (11) est fixée par un levier de retenue (8) en prise par enclenchement avec le levier de pression de soupape (11) et muni d'un élément de blocage (75), et
    en ce que le levier de retour (7) présente un tenon de déviation (80) qui peut être amené en liaison active avec une nervure de butée (77) du levier de retenue (8) de telle sorte que le levier de retenue (8) peut être amené depuis sa position de prise de blocage avec le levier de pression de soupape (11) dans la zone finale du mouvement de réglage du levier de retour (7) dans une position sans blocage du levier de pression de soupape (11).
  5. Dispositif selon la revendication 4, caractérisé en ce qu'il est prévu une levier de réglage (83) monté sur ressort, lequel est maintenu dans une position initiale inactive par l'élément de blocage (75) du levier de retenue (8), et
    en ce que le levier de retenue (8), après la libération du levier de pression de soupape (11) à la fin du mouvement de réglage du levier de retour (7), peut être amené par le tenon de déviation (80) dans une position de commutation dans laquelle le levier de réglage (83) est libéré, et
    en ce que le levier de réglage (83) exécute après sa libération un mouvement de réglage par lequel un élément de levier (85) supplémentaire peut être amené dans une position de pivotement active en vue d'ouvrir la soupape de sortie (30).
  6. Dispositif selon la revendication 5, caractérisé en ce que la position de pivotement active de l'élément de levier (85) est fixée par un levier de blocage (95) muni d'une languette de blocage (96) qui peut être amené en liaison flexible par enclenchement avec l'élément de levier (85), et
    en ce que le levier de blocage (95) présente un levier de déviation (97) qui se trouve dans la trajectoire de déplacement de la culasse lorsque le levier de blocage (95) se trouve en position de blocage, et
    en ce que le levier de blocage (95), par le mouvement de recul de la culasse (60), peut être amené dans une position neutre, ne bloquant pas l'élément de levier (85), par le biais d'une interaction de la culasse (60) avec le levier de déviation (97).
  7. Dispositif selon la revendication 6, caractérisé en ce que le levier de retour (7) présente un tourillon de réglage (102) qui peut être amené en liaison active avec un levier de rappel (103) du levier de réglage (83), et
    en ce que le levier de réglage (83), pendant le mouvement de recul du levier de retour (7) dans sa position initiale non déviée, peut être amené par le tourillon de réglage (102) dans sa position initiale du départ par le biais du levier de rappel (103).
EP10016002.7A 2010-05-04 2010-12-23 Système de recul pour armes à feu Not-in-force EP2385337B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202010006430U DE202010006430U1 (de) 2010-05-04 2010-05-04 Rückstoßsystem für Feuerwaffen

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EP2385337A2 EP2385337A2 (fr) 2011-11-09
EP2385337A3 EP2385337A3 (fr) 2013-12-25
EP2385337B1 true EP2385337B1 (fr) 2014-12-31

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DE102013225966A1 (de) 2013-12-13 2015-06-18 Thales Deutschland Gmbh Vorrichtung zur Simulation eines Rückstoßes einer Feuerwaffe und Feuerwaffe mit einer solchen Vorrichtung
DE102014200532A1 (de) 2014-01-14 2015-07-16 Thales Deutschland Gmbh Verfahren und Vorrichtung zum Wiederaufladen einer hydraulischen Vorrichtung zur Simulation eines Rückstoßes einer Feuerwaffe
DE102014201180A1 (de) 2014-01-23 2015-07-23 Thales Deutschland Gmbh Verfahren zum Trainieren der Benutzung und des Einsatzes von Feuerwaffen in einem Waffensimulator, Waffensimulator zur Ausführung eines solchen Verfahrens, zentraler Steuerrechner eines solchen Waffensimulators und Computerprogramm zum Ablauf auf einem solchen Steuerrechner
US9746273B2 (en) * 2014-11-14 2017-08-29 Pathfinder Systems, Inc. Recoil simulator and method for an imitation machine gun
DE102014225170A1 (de) 2014-12-08 2016-06-09 Thales Deutschland Gmbh Für Übungszwecke umgerüstete Feuerwaffe eines Waffensimulators
DE102015204809A1 (de) 2015-03-17 2016-09-22 Thales Deutschland Gmbh Feuerwaffe
DE102015211621A1 (de) 2015-06-23 2016-12-29 Thales Deutschland Gmbh Umgebaute Feuerwaffe, die Teil eines Waffensimulators ist und für Übungszwecke umgerüstet ist sowie Waffensimulator mit mindestens einer solchen umgebauten Feuerwaffe
DE102015211619B4 (de) 2015-06-23 2022-01-27 Thales Deutschland Gmbh Umgebaute Feuerwaffe, sowie Waffensimulator

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JP3529760B2 (ja) * 2001-11-06 2004-05-24 株式会社ウエスタン・アームス 模擬銃型光学手段制御装置
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Also Published As

Publication number Publication date
EP2385337A2 (fr) 2011-11-09
EP2385337A3 (fr) 2013-12-25
US20110275036A1 (en) 2011-11-10
US8496479B2 (en) 2013-07-30
DE202010006430U1 (de) 2010-08-19

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