EP2115377A1

EP2115377A1 - Control element, firing unit and firing assembly for a weapon

Info

Publication number: EP2115377A1
Application number: EP08715671A
Authority: EP
Inventors: Norbert Fluhr; Hermann Albrecht; Wolfgang Bantle; Johann August Bantle; Erwin Epp
Original assignee: Heckler und Koch GmbH
Current assignee: Heckler und Koch GmbH
Priority date: 2007-01-30
Filing date: 2008-01-30
Publication date: 2009-11-11
Anticipated expiration: 2028-01-30
Also published as: US20100037502A1; CA2675219C; WO2008092669A1; ZA200905219B; US8220192B2; EP2115377B1; DE102007004588B3; CA2675219A1; KR101284927B1; KR20090113837A; ES2393576T3

Abstract

The invention relates to a control element (50) for a hammer (3) that can be pivoted about a pivoting axis (7). The hammer can be locked in the loaded position with a counter-surface (29) of a release element (30, 31) by means of a detent surface (27). The hammer (3) has a control curve section (23), which, in a pivoting position that differs from the loaded position, engages with a control surface (32) of the release element (30, 31), holding the latter in an unlocked position. The control element (50) has a first control curve region (54), which is adjacent to the control curve section (23) and can be adjusted in the pivoting direction to expand said section and which engages with the control surface (32) in order to reduce the required pivoting space of the control curve section (23) and the control curve region (54) when the hammer (3) is moved from a firing position into the loaded position. The invention also relates to a firing unit comprising a control element (50) of this type in addition to an interchangeable firing assembly (1) comprising a hammer (3) and a trigger assembly that has a trigger bar (31), a detent surface (27), which acts by means of an elongated lever arm in relation to the pivoting axis (7), being located on the hammer (3). Said firing assembly (1) is compatible with an existing firing unit and is designed to be interchanged with the latter, the control curve (C) of the assembly having the same or less required pivoting space. The curve is traced by a hammer (A) of the firing assembly, said hammer having a detent surface (B) with a shorter lever arm acting in relation to the pivoting axis.

Description

Control, chopper and tee assembly for a weapon

The present invention relates to a control element for a percussion lever of a weapon which can be latched in its clamping position via a latching surface with a mating surface of a triggering element, for example a trigger lug on the trigger lever (see, for example, DE 198 46 657/2). At the hammer a cam portion is provided which engages in a deviating from the clamping position pivot position of the hammer on a control surface of the trigger element and this holds in an unlocked (non-securable) position.

Such a known mechanism prevents, for example in automatic rapid-fire guns, the incorrect operation of a safety device which acts on the trigger element.

The directional indications used below, such as front, back, top, bottom, right and left, are indicated from the point of view of a shooter holding the weapon.

In known mechanisms, the cam portion is usually formed as a circumferential surface, which is cam-shaped more or less concentric with the pivot axis or pivot shaft of the hammer.

The triggering element is usually formed in such weapons as a rocker arm having a sear at its (front) end and at the other (rear) end, for example, cooperates with corresponding control surfaces of a backup roll. Between the two ends of the rocker arm is pivotally mounted about a pivot axis defining the pivot axis and can be tilted about a trigger to trigger the hammer to the pivot point (when the weapon is unlocked). This dissolves the face the trigger lug from the catch surface of the hammer and the cam section passes over the edge of the trigger lug and holds the rocker arm on the control surface adjacent thereto - during the knock-down movement and in the stop position of the hammer - in the release position. The top of the sear serves as a control surface, which is pressed by the trigger spring against the cam section. In this position of the rocker arm, the backup roller, which acts on the other (rear) end, can not be adjusted. Thus, in a repeating or recharging the hammer can be pivoted freely in its clamping position.

This known mechanism ensures that the clamping operation is not affected - that is, a load-through of the weapon (automatically or manually) is possible and that during the clamping process, the trigger mechanism is not damaged. This would be the case if the triggering element were brought into a secured position via an accidental actuation of the securing roller with the impact lever removed. In such a secure position, namely, the clamping process of the hammer would be inhibited and it could trigger the deduction / knocking mechanism damage occurring. The principle of the abutment / securing mechanism described above is realized, for example, with the M16 rifle (see also, for example, US Pat. No. 5,713,150 A).

An important functional criterion in orderly weapons is the so-called trigger weight, which denotes the force required to confirm the triggering tackle. The deduction weight depends on several factors:

The trigger spring force with which the trigger lug is pressed into its latching position. And essentially of the frictional force acting between the locking surface on the hammer and the corresponding counter surface on the trigger element - the end face of the sear. This frictional force must be overcome to bring the sear out of engagement with locking surface on the hammer. This frictional force depends on the orientation of the active surfaces in engagement (latching surface and end face), the coefficient of friction acting between the two surfaces and the force with which the latching surface is pressed against the trigger lug. This force, in turn, depends on the spring force of the spring element acting on the impact element and on the effective lever arm, which defines the effective distance of this latching surface from the pivot axis of the striking piece. With the same spring force acting on the striking piece, the friction force increases the closer the locking surface is arranged on the pivot axis of the striking piece. In other words, the shorter the effective lever arm, the higher the frictional force.

This lever arm also largely determines the pivot space requirement of the control cam section, which starts from the triggering edge of the latching surface and, with a short lever arm, runs close to the pivot axis and with a long lever arm further away from the pivot axis.

Comparatively high "takeoff weights" of 35 to 40 N (3.5-4 kp) can affect the shot accuracy. Better are deduction weights that are lower - for example in the range of 15-20 N (1.7 - 2 kp).

In order to reduce the trigger weight corresponding to an existing weapon, there are several possibilities: It is possible, for example, the Gleitflächenpaarung and thus the effective coefficient of friction between the locking surface on the hammer and the counter surface on the sear by appropriate surface treatments (grinding, polishing, coating , etc.). However, such a process is technically complex and possibly - conditional due to the high stress of this sliding surface pairing - not even permanently.

It is also possible to change the orientation of the latching surface and the counter surface on the sear to each other, so that the tendency of these two surfaces to interlock with each other is reduced. Although this measure reduces the friction, however, it can only be realized with a high manufacturing outlay (tight production tolerances). There may also be the risk that a reliable locking no longer takes place, and possibly a shot by external influences (shocks, shocks, etc.) solves.

Another approach is to lower the trigger spring force. Thus, the frictional force acting on the Gleitflächenpaarung is reduced accordingly and reduced the deduction weight. However, a reduced spring force acting on the impact piece involves the risk that the impact effect is reduced to such an extent that, in the worst case, the ammunition to be fired is no longer reliably ignited.

All the above-mentioned measures require high manufacturing precision in order to accurately and repeatably set a low trigger weight on different weapons and to maintain constant over a long period of operation without costly maintenance.

Another way to change the trigger weight, is to vary the effective lever arm, with which the locking surface on the mating surface (the end face of the Abziehsstollens) attacks. About this measure, the desired effect and thus the friction can be controlled comparatively precise without the production cost would have to be significantly increased.

Fig. 5 shows a hammer A, in which, starting from a dashed lines shown latching and control contour B and C a modified locking and control contour E and F is provided, in which by an extension of the effective lever arm from h to H, the withdrawal force has been reduced. At the same time, Fig. 5 illustrates a problem occurring; namely, that the swivel space requirement of the cam portion E has increased compared to that of the cam portion B. Under certain circumstances, this swivel space requirement increases to the extent that the existing space conditions in the weapon housing are no longer sufficient to realize this solution. That is, with existing weapons, this measure to reduce the trigger weight is difficult to achieve because a suitably modified hammer in the existing housing does not accommodate (collision area K). Additional modifications (milling, extensions, etc.) are required.

A corresponding flattening of the cam portion to avoid the collision K (black area shown) with the weapon housing would not solve the problem, because then a significant cam section would be missing, which prevents the trigger element in the teeing position of the trigger is tilted so that an accidental backup can be excluded (see above).

On this basis, there is the object of providing a knock-off device or a bumping module, in which a lower trigger weight is possible, without thereby affecting other core functions of the trigger / securing mechanism. It should not be extended to the extent possible space requirement.

This object is achieved by the control according to claim 1.

The invention is characterized in that the control element has a first cam portion, which is adjustable in the pivoting direction to the cam portion of the Impact lever adjacent. The control is adjustable so that it depending on the pivot position of the hammer the cam portion in the pivoting direction, ie in the circumferential direction, optionally extended and engages in corresponding pivot positions on the control surface of the trigger element and thus retains the required arming function in the desired pivoting range of the hammer. Due to the adjustability of the control element and its cam portion of the required cam section can be reduced on the hammer and thus also the required pivot space requirement for this reduced cam section. However, the control function is realized for the complete pivoting of the hammer on the control surface of the trigger element and in particular in the tee position of the hammer.

With such a control element, the stripping device according to claim 9 can be realized, or a striker assembly according to claim 10, in which the stripping weight is reduced by providing a detent surface acting on the striker lever about an extended lever arm to the stripping shaft. Such a tee assembly is interfaceable to an existing chopper and designed to be interchangeable. In this case, the required pivoting space requirement is not extended, so that a tee-off assembly is also suitable as a retrofit kit for an existing weapon.

According to claim 2, the control element is designed as a coaxial with the pivot axis of the pivot lever pivotable cam. By this measure, the control is to be arranged close to the control cam portion supporting portion of the pivot lever. The cam portion of the cam may be formed directly adjacent to the cam portion and in this transitional. Such a cam can be made as a simple stamping. According to claim 3, the control on a second cam portion which engages the clamping position einnehmendem hammer on the trigger element and thus sets the locking depth between the locking surface on the hammer and the counter surface on the control. This simplifies the production of the hammer. Only the locking surface and the effective cam section need to be processed accurately. The second cam portion serves as a stop for the depth of engagement of the end face of a sear. The depth of engagement determines the overlap (the coupling surface) of the active surfaces and thus also the frictional force acting between these surfaces and thus also the deduction weight. Over different radii of the second cam section so the deduction weight can be adjusted further.

The claims 4 to 7 relate to measures with which the required adjustability of the control to the hammer in response to its pivot position can be realized. According to claim 4, for this purpose, the control element has a setting region which, at a counterpart (for example catch region of the pivoting lever), stops the pivoting position relative to the striking lever. In this case, a first adjusting range is provided according to claim 5, which strikes the clamping area on the driver area and adjusts the control in the desired manner. In the present case, this can take place in such a way that the control curve zone formed from the control curve section and the control curve section is shortened and thus the swivel space requirement is minimized.

In accordance with claim 6, a second adjustment range is provided, which acts in opposite directions and ensures that the control curve zone is extended at tee-off or when the hammer is cut off and exerts the control function. In accordance with claim 7, a third adjustment range is provided to finally set the final position between the control element and hammer in teeing position and thus also the maximum extent of the control curve zone. The pivot sleeve on the control element according to claim 8, which is coaxially mounted on the pivot shaft of the hammer, allows a clean management and investment of the control - especially a cam - on the Schlaghebelflanke, ensures the required pivoting movement and prevents tilting of the control on the pivot shaft. The use of such a sleeve also allows a relatively generous tolerance between the sleeve inner surface and the pivot shaft outer surface.

Claim 9 relates to a chopping device with a control according to the invention. Claims 10 and 11 relate to a complete tee-off assembly according to the invention, which is completely interchangeable with an existing tee-off device, so that a reduced trigger weight can be realized without further intervention and conversion measures on an existing weapon, without important safety and functional aspects being impaired.

According to claim 11, such a tee assembly may additionally have a trigger, a breaker and a continuous fire jack, so that the tee assembly is particularly suitable for semi-automatic or automatic ordnance weapons.

Claim 12 finally relates to a weapon which is provided with a corresponding control of a knock-off device or a tee-off assembly.

An embodiment of the present invention will now be explained with reference to the drawings. Showing:

1 is a perspective view of a tee assembly or device with a control according to the invention, Fig. 2 is a partial view of the exhaust area of a

Weapon with partially exposed trigger mechanism in clamping position,

3 shows the view from FIG. 2 with the trigger mechanism in the release position, FIG.

Fig. 4 shows the illustration of FIG. 3 without control, and

Fig. 5 is an illustration of a modified conventional chopper in which a modified hammer collides with the weapon housing.

Fig. 1 shows a knockout or a tee assembly 1 with the hammer 3 in clamping position. 2 shows the same arrangement in a weapon housing 5. The illustrated impact lever 3 is seated on a pivot shaft 9 defining the pivot axis 7 and received in the housing 5. A leg spring arrangement 11 acts between a stop 13 and the impact lever 3 and biases it in the direction of impact, so that when the striking lever is triggered, it strikes with its striking surface 15 against a firing pin (not shown) and ignites a propellant charge (knock-out position: see FIG 3).

The illustrated impact lever 3 is further provided with a catch nose 17 which cooperates with a breaker 19. At the rear end of the percussion lever 3 a Dauerfeuerklinke 21 is arranged.

At the front end of the percussion lever 3 of the cam-like cam portion 23 which is connected via an edge 25 with the perpendicular to the cam portion 23 extending locking surface 27 (Fig. 3), via which the Whip lever 3 is held in its detent position (Fig. 1, Fig. 2).

The latching takes place via the end face 29 of the latching lugs 31 designed as the end of the trigger lever 33. The trigger lever 33 is pivotally mounted on the trigger shaft 35 in the weapon housing 5 and the trigger spring 37 (here also designed as a leg spring assembly) with its front end or the latching lug 31 upwards in the direction of hammer 3. In this case, the end face 29 and the locking surface 27 engage each other so that the hammer 3 is held in the cocked position. The serving as a backup end rear end 39 of the trigger lever 33 engages in corresponding cam portions 44 of the backup roller 40, which is rotatable on the outside of the housing extending operating lever 41.

On the underside of the trigger lever 33, the trigger blade 42 protrudes and protrudes from the weapon housing 5 in the trigger guard area 43. To trigger the trigger blade 42 is actuated. In this case, the trigger lever 33 is pivoted against the action of the trigger spring 37 and the latching lug 31 is disengaged from the hammer 3. More specifically, the end face 29 slides along the latching surface 27 until the trigger edge 30 passes under the edge 25 and the hammer 3 quick action under the action of the leg spring assembly 11 in the tee position (Figures 3 and 4).

On the left side flank of the hammer 3, a control element is arranged, which is designed as a flat cam disc 50 and also sits on the sleeve 52 pivotally mounted on the pivot shaft 9.

The cam disk 50 is laterally adjacent to the control cam portion 23 with its first cam portion 54 and extending in the circumferential direction. A second

Cam section 56 engages in the clamping position of the Impact lever 3 at the trigger edge 30 and at the outgoing therefrom control surface 32 and sets the depth of engagement of the Raststollens 31 and the end face 29 on the latching surface 27 fixed.

The rotational position of the control element 50 with respect to the impact lever 3 in the tensioning position is determined by the first control range 58, which rests against a driving shoulder 22 of the striking lever 3 and prevents further rotation of the cam disk 50 to the striking lever 3 (in FIG. 2 rotation of the cam disk 50 counterclockwise to the hammer 3).

A second adjustment range 60 limits the rotational position of the cam disc 50 with respect to the impact lever 3 in the other direction when it moves from its clamping position into the knock-off position (see FIG. 3).

The following happens: After uncoupling the trigger edge 30 of the edge 25 of the percussion lever 3 jumps forward and possibly twisted against the cam plate 50 (the cam 50 shifts in the clockwise direction with respect to the hammer 3), until the second setting range At the end of the pivotal movement of the hammer 3 - which now takes the tee position - proposes the cam plate 50 with the third adjusting portion 62 on the housing wall 6 at.

The cam disk 50 thus rotates during the knock-off movement of the hammer 3 in the clockwise direction to this. In this case, the first cam portion 54 is displaced in the circumferential direction to the control cam portion 23. Thus, the trigger edge 30 and the control surface 32 (the top of Raststollens 31) now only on the cam portion 54 of the cam plate 50 and presses on the detent Stollen 31 the trigger lever 33 in the position shown in Fig. 3.

In this position, the cam portion 54 pushes the locking lug 31 down and thereby the rear end 39 of the trigger lever 33 upwards and engages in the corresponding cam portion 44 of the backup roller 40 a. The cam portion 44 is formed so that it can not be moved from the illustrated in Fig. 3 unlocked position (rear end 39 above) in the securing position shown in Fig. 2 (rear end 39 below).

This mechanism ensures that when repeating the hammer 3 can be brought back into its cocked position. Without the cam disc 50 serving as a control, the trigger lever 33 would in fact be pressed by the trigger spring 37 into the position shown in FIG. The rear end 39 of the trigger lever 33 would be in a position in which the backup roller 40 can be brought into the secured position. In the secured position, the cam portion 44 blocks the trigger lever 33. The latching lug 31 would block the hammer 3 in this position. He could not be tense or would damage the trigger lever 33 when tightening or possibly cancel the catches 31.

At the same time, such a control element (in this case the cam disc 50) reduces the pivoting space requirement of the control cam section 23. This is so shortened that it does not reach the region of the housing wall 6 delimiting the pivot space when the striking lever 3 is pivoted into the clamping position. In other words, the control element (here the cam disc 50) allows a relatively long lever arm between pivot axis 7 and latching surface 27. This allows a reduced trigger weight against a locking surface, which is arranged closer to the pivot axis 7 (see also the explanations in the introductory part to Fig. 5). When pivoting the hammer 3 from the teeing position in the cocked position namely cam disk 50 and hammer 3 rotate again to each other until the Mitnehmerabsatz 22 abuts the first setting range 58. The cam section 23 engages the triggering edge 30 or the control surface 32 and the cam disk 50 and impact lever 3 move together into the clamping position (FIG. 2), in which the latching lug 31 passes behind the latching surface 27. The pivot space between hammer 3 and housing wall 6 is sufficient. There is no collision. Depending on the pivot position of the hammer 3, the cam disc 50 is displaced. The control curve zone formed from the control cam section 23 and the first cam section 54 is shortened (clamping position Fig. 2) or extended (teeing position Fig. 3). The available swivel space area is used optimally.

In this way, a stripping device or a stripping assembly 1 can be realized, which can be exchanged as a replacement unit for a corresponding assembly with a shorter effective lever arm. The bearings of the pivot shaft 9 and the take-off shaft 35 need not be changed. The tee-off force does not have to be reduced. Such a replacement module can also be set up so that it can be equipped with further known locking mechanisms (interrupter 19, continuous emergency release 21) which cooperate with an existing backup roller 40. Optionally, the backup roller 40 can be exchanged with such a unit with.

Further variations and modifications of the present invention will become apparent within the scope of the appended claims.

Claims

claims

1. control element (50) for a pivot axis (7) movable hammer (3), which in its clamping position via a latching surface (27) with a counter surface (29) of a trigger element (30, 31) can be latched, and a cam portion ( 23), which engages in a pivoting position deviating from the clamping position on a control surface (32) of the trigger element (30, 31) and holds it in an unlocked position, wherein the control element (50) has a first cam portion (54) which in Swivel direction adjustable adjacent to the cam portion (23), this extends depending on the pivot position in the pivoting direction and the control surface (32) engages the pivotal space requirement of the cam portion (23) and the Steurkurvenbereichs (54) when adjusting the hammer (3) from a Reduce teeing position in the clamping position.

Second control element (50) according to claim 1, which is designed as a coaxial with the pivot axis (7) of the hammer (3) pivotable cam disc.

3. control element (50) according to claim 1 or 2, which has a second cam portion (56) which engages the clamping position engaging hammer (3) on the trigger element (30, 31) and the detent depth between locking surface (27) and counter surface (29 ) Are defined.

4. Control (50) according to one of claims 1 to 3, which has a control range (58, 60, 62), depending on the pivot position of the hammer (3) on a counterpart (26, 6) abutting the pivot position to the hammer (3 ) limited .

5. control (50) according to claim 4, wherein a first adjusting portion (58) for abutment against a driver portion (22) on the hammer (3) is formed during the clamping operation and in the clamping position.

6. Control element (50) according to claim 4 or 5, in which a second setting region (60) for abutment on the driver region (22) of the striking lever (3) is formed during the knocking process.

7. control (50) according to one of claims 4 to 6, wherein a third adjusting portion (62) for abutment on a housing component (6) is formed to see the end position between control (50) and hammer (3) in teeing position set.

8. Control (50) according to any one of claims 1 to 7, with a pivot sleeve (52) which is coaxial on a pivot shaft (9) of the hammer (3) attachable.

9. knock-over device (1) with a control element (50) according to one of claims 1 to 8, which is arranged coaxially to a pivot shaft (9) of a striking Hebeis (3) and its first cam portion (54) in the teeing position of the hammer ( 3) engages a latching lug (31) of a trigger lever (33), so that it engages with its securing end (39) in a securing device (40, 43) such that it can not be adjusted to a secured position.

10. tee assembly (1) with a control element (50) according to one of claims 1 to 8, a hammer (3) and a trigger lever (33) having trigger assembly, wherein the impact lever (3) is arranged around a prolonged lever arm to the pivot axis (7) acting detent surface (27), wherein the tee assembly (1) is interface compatible to a knockout and exchangeable against this and the same or a smaller swivel space requirement of a control cam ( C), which is arranged on a hammer (A) of the knock-off device, in which a latching surface (B) with a shorter lever arm acts to the pivot axis.

11. A tee assembly (1) according to claim 10, additionally comprising a trigger tongue (42), a breaker (19) and a Dauerfeurklinke (21).

12. weapon with a control (50) according to any one of claims 1 to 8, a knock-off device (1) according to claim

9 or a tee assembly (1) according to claim 10 or 11.