EP2115377A1 - Élément de commande, mécanisme de tir et module de tir destinés à une arme - Google Patents

Élément de commande, mécanisme de tir et module de tir destinés à une arme

Info

Publication number
EP2115377A1
EP2115377A1 EP08715671A EP08715671A EP2115377A1 EP 2115377 A1 EP2115377 A1 EP 2115377A1 EP 08715671 A EP08715671 A EP 08715671A EP 08715671 A EP08715671 A EP 08715671A EP 2115377 A1 EP2115377 A1 EP 2115377A1
Authority
EP
European Patent Office
Prior art keywords
hammer
control
trigger
lever
pivot
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08715671A
Other languages
German (de)
English (en)
Other versions
EP2115377B1 (fr
Inventor
Norbert Fluhr
Hermann Albrecht
Wolfgang Bantle
Johann August Bantle
Erwin Epp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Heckler und Koch GmbH
Original Assignee
Heckler und Koch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Heckler und Koch GmbH filed Critical Heckler und Koch GmbH
Publication of EP2115377A1 publication Critical patent/EP2115377A1/fr
Application granted granted Critical
Publication of EP2115377B1 publication Critical patent/EP2115377B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F41A19/00—Firing or trigger mechanisms; Cocking mechanisms
    • F41A19/06—Mechanical firing mechanisms, e.g. counterrecoil firing, recoil actuated firing mechanisms
    • F41A19/42—Mechanical firing mechanisms, e.g. counterrecoil firing, recoil actuated firing mechanisms having at least one hammer
    • F41A19/43—Mechanical firing mechanisms, e.g. counterrecoil firing, recoil actuated firing mechanisms having at least one hammer in bolt-action guns
    • F41A19/44—Sear arrangements therefor
    • F41A19/45—Sear arrangements therefor for catching the hammer after each shot, i.e. in single-shot or semi-automatic firing mode
    • 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
    • F41A19/00—Firing or trigger mechanisms; Cocking mechanisms
    • F41A19/06—Mechanical firing mechanisms, e.g. counterrecoil firing, recoil actuated firing mechanisms
    • F41A19/14—Hammers, i.e. pivotably-mounted striker elements; Hammer mountings

Definitions

  • 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).
  • 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.
  • 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.
  • 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.
  • the backup roller which acts on the other (rear) end, can not be adjusted.
  • 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).
  • 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 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 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.
  • 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.
  • 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 Abziehss Hecks) 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.
  • 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).
  • 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.
  • 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.
  • 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.
  • the control element is designed as a coaxial with the pivot axis of the pivot lever pivotable cam.
  • 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.
  • the control on a second cam portion which engages the clamping position ein mecanicdem 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • FIG. 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
  • FIG. 3 shows the view from FIG. 2 with the trigger mechanism in the release position
  • Fig. 4 shows the illustration of FIG. 3 without control
  • 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.
  • a Mama85klinke 21 is arranged at the rear end of the percussion lever 3 .
  • 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.
  • 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.
  • the trigger blade 42 protrudes and protrudes from the weapon housing 5 in the trigger guard area 43.
  • 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).
  • a control element 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.
  • 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 Raststechnischs 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 cam disk 50 thus rotates during the knock-off movement of the hammer 3 in the clockwise direction to this.
  • the first cam portion 54 is displaced in the circumferential direction to the control cam portion 23.
  • the trigger edge 30 and the control surface 32 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.
  • 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.
  • control element in this case the cam disc 50
  • the control element 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).
  • 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.
  • the backup roller 40 can be exchanged with such a unit with.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Toys (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Electrophonic Musical Instruments (AREA)

Abstract

La présente invention concerne un élément de commande (50) destiné à un chien (3) pouvant pivoter autour d'un axe de pivotement (7). Selon l'invention, le chien peut être bloqué dans sa position d'armé par une surface d'arrêt (27) avec une contre-surface (29) d'un élément de détente (30, 31). Le chien (3) présente une section de commande courbe (23) qui, dans une position de pivotement différente de la position d'armé, vient en prise avec une surface de commande (32) de l'élément de détente (30, 31) et maintient celui-ci dans une position sans sûreté. L'élément de commande (50) présente une première zone de commande courbe (54) qui est adjacente à la section de commande courbe (23) en pouvant être réglée en direction de pivotement, élargit ladite section en direction de pivotement en fonction de sa position de pivotement et vient en prise avec la surface de commande (32) pour réduire l'espace de pivotement nécessaire à la section de commande courbe (23) et à la zone de commande courbe (54) lors du passage du chien (3) de la position de tir à la position d'armé. L'invention concerne également un mécanisme de tir comprenant un élément de commande (50) de ce type et un module de tir (1) interchangeable comprenant un chien (3) et un module de détente présentant une gâchette (31), une surface d'arrêt (27) qui agit autour d'un bras de levier allongé en direction de l'axe de pivotement (7), se trouvant sur le chien (3). Ce module de tir (1) est conçu pour être compatible via une interface avec un mécanisme de tir et pour pouvoir être échangé contre celui-ci, et présente le même espace de pivotement ou un espace de pivotement inférieur à celui nécessaire à une courbe de commande (C) qui se trouve sur un chien (A) du mécanisme de tir, une surface d'arrêt (B) qui présente un bras de levier plus court, agissant en direction de l'axe de pivotement.
EP08715671A 2007-01-30 2008-01-30 Élément de commande, mécanisme de tir et module de tir destinés à une arme Not-in-force EP2115377B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007004588A DE102007004588B3 (de) 2007-01-30 2007-01-30 Steuerelement, Abschlageinrichtung und Abschlagbaugruppe für eine Waffe
PCT/EP2008/000732 WO2008092669A1 (fr) 2007-01-30 2008-01-30 Élément de commande, mécanisme de tir et module de tir destinés à une arme

Publications (2)

Publication Number Publication Date
EP2115377A1 true EP2115377A1 (fr) 2009-11-11
EP2115377B1 EP2115377B1 (fr) 2012-08-29

Family

ID=39406933

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08715671A Not-in-force EP2115377B1 (fr) 2007-01-30 2008-01-30 Élément de commande, mécanisme de tir et module de tir destinés à une arme

Country Status (8)

Country Link
US (1) US8220192B2 (fr)
EP (1) EP2115377B1 (fr)
KR (1) KR101284927B1 (fr)
CA (1) CA2675219C (fr)
DE (1) DE102007004588B3 (fr)
ES (1) ES2393576T3 (fr)
WO (1) WO2008092669A1 (fr)
ZA (1) ZA200905219B (fr)

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US7654187B2 (en) 2004-04-30 2010-02-02 Colt Defense Llc Firearm fire control selector
DE102010054984A1 (de) * 2010-12-18 2012-06-21 Schmeisser Gmbh Schlagstück für eine Handfeuerwaffe
DE202011004556U1 (de) * 2011-03-30 2012-07-04 Sig Sauer Gmbh Abzugseinrichtung für eine Handfeuerwaffe
DE102011107750A1 (de) * 2011-07-15 2013-01-17 Schmeisser Gmbh Sicherungseinrichtung zur Befestigung von Stiften an einer Waffe
US9175917B2 (en) * 2013-12-03 2015-11-03 Terrence Dwight Bender Trigger with cam
DE102014107620B3 (de) 2014-05-30 2015-02-19 Merkel Jagd- Und Sportwaffen Gmbh Handfeuerwaffe und Abzugssicherung hierfür
US10006733B2 (en) 2014-10-22 2018-06-26 In Ovation Llc Non-fouling trigger
US10330413B2 (en) 2016-08-11 2019-06-25 Springfield, Inc. Half-cock trigger safety assembly
USD828895S1 (en) 2016-09-28 2018-09-18 WHG Properties, LLC Trigger mechanism
US9927197B1 (en) * 2016-09-28 2018-03-27 WHG Properties, LLC Trigger mechanism for a firearm
US10837728B2 (en) 2018-02-20 2020-11-17 Krl Holding Company, Inc. Two-stage, drop-in trigger assembly
DE102019104346A1 (de) 2018-02-20 2019-08-22 Krl Holding Company, Inc. Zweistufige Drop-In-Abzugseiheit
US11530889B1 (en) * 2019-09-22 2022-12-20 Fcip Llc Firearm, trigger assembly, and trigger assembly hammer
US11592255B2 (en) 2020-01-20 2023-02-28 In Ovation Llc Fire control assembly
US11927408B2 (en) 2020-01-20 2024-03-12 In Ovation Llc Fire control assembly
DE102021103878B8 (de) 2021-02-18 2022-06-23 Heckler & Koch Gmbh Steuerelement, Verschlussfanghebel, Verschlussträger, Abzug, Abzugsbaugruppe für eine Maschinenwaffe sowie damit ausgestattete Maschinenwaffe

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US1387369A (en) 1920-08-24 1921-08-09 Firm Of Oesterreichische Waffe Gun-lock for automatic firearms
DE2311105A1 (de) * 1973-03-06 1974-09-12 Walter Gehmann Abzugseinrichtung fuer schusswaffen
US5166458A (en) 1991-01-11 1992-11-24 Daewoo Precision Ind., Ltd. Firing mechanism for fast shooting pistol
US5713150A (en) * 1995-12-13 1998-02-03 Defense Technologies, Llc Combined mechanical and Electro-mechanical firing mechanism for a firearm
DE19716100A1 (de) * 1997-04-17 1998-10-22 Peter Ebenberger Abzugseinrichtung für Handfeuerwaffen mit vermindertem Abzugsgewicht
DE19732857C1 (de) 1997-07-30 1998-10-08 Heckler & Koch Gmbh Spannabzugseinrichtung mit einer Hammersicherung
DE19846657C2 (de) * 1998-10-09 2001-02-15 Heckler & Koch Gmbh Abschlageinrichtung mit vermindertem Abzugsgewicht
DE202005020845U1 (de) * 2004-09-29 2006-09-28 Carl Walther Gmbh Pistolen-Abzugs-Vorrichtung
CA2590831A1 (fr) * 2004-12-16 2006-06-16 New Colt Holding Corporation Pistolet modele 1911 a double action
US20060207147A1 (en) * 2005-03-19 2006-09-21 Lazor Ernest R Self-contained triggerplate action for low profile firearms

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Also Published As

Publication number Publication date
US8220192B2 (en) 2012-07-17
US20100037502A1 (en) 2010-02-18
WO2008092669A1 (fr) 2008-08-07
CA2675219A1 (fr) 2008-08-07
DE102007004588B3 (de) 2008-07-24
KR101284927B1 (ko) 2013-07-10
KR20090113837A (ko) 2009-11-02
ZA200905219B (en) 2010-03-31
CA2675219C (fr) 2011-05-03
EP2115377B1 (fr) 2012-08-29
ES2393576T3 (es) 2012-12-26

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