EP1179172A1 - Dispositif de reglage pour un systeme d'arme a feu - Google Patents

Dispositif de reglage pour un systeme d'arme a feu

Info

Publication number
EP1179172A1
EP1179172A1 EP00940253A EP00940253A EP1179172A1 EP 1179172 A1 EP1179172 A1 EP 1179172A1 EP 00940253 A EP00940253 A EP 00940253A EP 00940253 A EP00940253 A EP 00940253A EP 1179172 A1 EP1179172 A1 EP 1179172A1
Authority
EP
European Patent Office
Prior art keywords
adjustment
actuator
eccentric
module
line
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
EP00940253A
Other languages
German (de)
English (en)
Other versions
EP1179172B1 (fr
Inventor
Johannes Murello
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 EP1179172A1 publication Critical patent/EP1179172A1/fr
Application granted granted Critical
Publication of EP1179172B1 publication Critical patent/EP1179172B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F41—WEAPONS
    • F41G—WEAPON SIGHTS; AIMING
    • F41G1/00—Sighting devices
    • F41G1/38—Telescopic sights specially adapted for smallarms or ordnance; Supports or mountings therefor
    • F41G1/387—Mounting telescopic sights on smallarms
    • 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
    • F41A21/00—Barrels; Gun tubes; Muzzle attachments; Barrel mounting means
    • F41A21/06—Plural barrels
    • F41A21/08—Barrel junctions

Definitions

  • the invention relates to a device for adjusting the mutual position of two modules of a firearm system.
  • firearm system encompasses single-barrel or multi-barrel firearms, which can additionally be combined with an attachment device, such as an optical aiming device or another firearm.
  • a “module” is understood in particular to mean a run or a target device or its longitudinal axes. However, it can also be any other component of a firearm system or its axis.
  • Such an insert barrel is usually set up for a caliber-sized bullet cartridge and is used in a shotgun barrel of a combined weapon, such as a triplet. There the insertion run must be adjusted so that its meeting point coincides with the stopping point of the weapon sight, which is shot on the barrel of the gun.
  • the rear part of the insert is radially free of play but easily pivotable in the cartridge chamber of the shotgun barrel and a ring is arranged on the front part of the insert barrel which is spaced from the inner wall of the shotgun barrel.
  • this ring Over its circumference, this ring has four radial threaded bores, each offset by 90 °, the axes of which run along the horizontal or vertical.
  • grub screws In the threaded bores there are grub screws which have to be screwed out or in when the weapon is fired in such a way that the outer ends of the grub screws are firmly supported on the inner wall of the shotgun barrel when the barrel has reached the desired angular position.
  • a firearm is known with an insert barrel inserted therein, which can be aligned with the barrel receiving it by means of a rotatable and displaceable eccentric bushing in the barrel longitudinal direction.
  • an insertion weapon barrel for installation in a battle tank weapon barrel is also known, the desired direction of which can be set via two axially immovable eccentric bushings running into one another.
  • the invention has for its object to provide a further adjustment device of the type mentioned, the space requirement is small, but still allows effortless adjustment to the side and height.
  • the invention chooses a rotatable eccentric adjustment which enables a linear displacement of at least one module or of a member engaging thereon.
  • a pivoting of the module can then be easily realized by suspending it pivotably at a first bearing point, and displacing it at a second bearing point by the member acting on it.
  • the subject matter of claim 1 relates to a device for adjusting the mutual position of at least a first and second module of a firearm system with the following features ao: At least one first rotatable adjustment eccentric is in operative connection with at least the first module in such a way that by rotating this adjustment eccentric, the first module can be displaced relative to the second module along a first adjustment line or pivoted within a first adjustment plane.
  • adjusting eccentric encompasses any type of body, the outer shape of which is designed to load a module or actuator lying thereon in the direction of the respective adjustment line or adjustment plane when the body is rotated.
  • a protuberance or cam can also be attached to the outside of the adjustment eccentric.
  • modules can be adjusted to each other, such as rear sight or front sight to barrel, telescopic sight to barrel or barrel to barrel (or their longitudinal or core axes).
  • modules can also be adjusted relative to one another.
  • the soul axes of several barrels of a firearm can be connected to one another or to another axis, e.g. the line of sight of a riflescope.
  • Said displacement or pivoting of the first module is preferably carried out (according to claim 2) via a first actuator which is operatively connected to the first module and the first adjustment eccentric in such a way that the first actuator along the first adjustment straight line is rotated by rotating the first adjustment eccentric is movable.
  • the actuator is therefore, at least in functional terms, arranged between the first module and the first adjustment eccentric.
  • the actuator can be cohesively connected to the module and thus form an emneit with it.
  • the device has a second adjustment eccentric, which can be rotated independently of the first adjustment eccentric, and is also operatively connected to at least the first module in such a way that the first module is rotated relative to the second by rotating the second adjustment eccentric Module can be moved along a second adjustment line or can be pivoted within a second adjustment plane.
  • the two adjustment lines or adjustment planes are not aligned parallel, but preferably orthogonally to one another. In this way, the modules can be adjusted separately according to height and side, namely by turning the first or second adjustment eccentric (or vice versa).
  • the first actuator is also operatively connected to the second adjustment eccentric in such a way that the first actuator can be displaced along the second adjustment line by rotating the second adjustment eccentric.
  • the displacement or pivoting of the first module along the two adjustment lines or within the two adjustment levels takes place solely via the first actuator.
  • the displacement or pivoting of the first module can thus be brought about via a single bearing point, namely where the first module is in operative connection with the first actuator.
  • a still further development provides a second actuator via which the first actuator is displaced along the second adjustment line.
  • the second actuator is connected to the second adjustment eccentric and the first actuator in such a way that by rotating the second adjustment eccentric the second actuator can be moved along the second adjustment line and thereby also moves the first actuator in the same direction. Moving the first actuator lengthways the first adjustment line is again via the first adjustment eccentric, regardless of the second actuator.
  • the adjustment eccentrics are preferably designed (according to claim 6) as cam disks.
  • a solcne cam is any disk or ring-like body with a curved outer contour, the distance to the center of rotation of the body varies.
  • the first and / or second adjustment eccentric is designed as an eccentrically mounted circular disk.
  • the associated actuators are then preferably designed and arranged so that they are permanently and without play at exactly two contact points on the outside of the first or second circular disk, the contact points being the intersection points of the respective circular disk with a first or are second straight lines that run through the center of the circular disk and are aligned parallel to the first or second adjusting straight lines. Permanent here means that the actuators remain in constant contact with the respective circular disk when it rotates. At exactly two contact points means that this contact only exists at these points, that is to say the actuators are spaced apart from the remaining circumference of the circular disk. In this way, the associated actuator is loaded only in the direction of its adjustment line by the movement of the circular disks, that is to say by turning the adjustment eccentric.
  • the first and / or second adjustment eccentric are mounted on an axis that is stationary relative to the weapon housing.
  • This axis can be the longitudinal axis of the first module, e.g. the soul axis of a barrel rigidly connected to the gun case.
  • At least one of the two adjustment eccentrics (according to claim 10) consists of two or more detachably connected inputs parts. This is done, for example, for assembly reasons if an adjustment eccentric is extended in the axial direction and thereby engages under other components arranged on this axis.
  • first or second guide means are preferably guided (according to claim 11) by first or second guide means along their respective adjustment straight lines. In this way, if necessary, e.g. in the event of insufficient guidance by the adjustment eccentrics, the directions of displacement of the actuators are mandatory.
  • the guide means are preferably designed (according to claim 12) as part of the movable arrangement of the actuators.
  • the first guide means of the first actuator are rigidly connected to the second actuator.
  • a displacement of the first actuator relative to the second actuator is only possible along the first adjustment line. This also has the consequence that when the second actuator is moved, the first actuator is also moved along the second adjustment line.
  • the second actuator is also preferably guided (according to claim 14) by means of second guide means which are rigidly connected to the gun housing.
  • any type of active connection that is suitable for prescribing the direction of movement and / or position of the actuators when they are displaced can be used as guide means.
  • any type of active connection that is suitable for prescribing the direction of movement and / or position of the actuators when they are displaced can be used as guide means.
  • the first or second guide means is designed as a tongue and groove connection.
  • the tongue and groove connection can e.g. be designed as a dovetail in order to anchor the respective actuator also in the axial direction.
  • the securing means can be designed differently depending on the space requirement and the forces to be absorbed.
  • a simple option are positive locking devices, such as a spring steel washer, which loads the adjustment eccentric in the axial direction.
  • Another example are clamp connections, by means of which the adjustment eccentrics are held in their set position.
  • form-fitting connections come as a means of securing the question.
  • the securing means comprise a locking disk and at least one locking bolt per adjustment eccentric, which is operatively connected to the respective adjustment eccentric and engages in suitable recesses in the rotating or stationary locking disk.
  • Different adjustment positions can be specified by suitably arranging several recesses.
  • the locking bolts are preferably spring-loaded so that they automatically snap into the recesses.
  • the connection between the locking pin and the locking disc can then be designed such that the locking pin must be manually pulled out of the recess for further adjustment of the respective adjusting eccentric or yields by itself if the torque is sufficiently high.
  • the latter option simplifies the adjustment process, but for a securing of the adjustment eccentric it presupposes that the spring force is adapted to the forces occurring on the weapon side
  • At least one adjustment eccentric can engage the locking disc directly, for example by means of a fixed locking bolt or a suitable toothing.
  • the axial securing of the adjustment eccentric eg a locking ring, must then be removed manually for adjustment.
  • two or more adjustment positions are predetermined by the securing means, in such a way that by rotating the adjustment eccentric from one adjustment position to the next, the first or second actuator along their adjustment lines (x, y) by respectively same distance can be moved.
  • the two modules can be displaced or pivoted with respect to one another with constant steps, which considerably simplifies the adjustment process.
  • Figure 1 is a sectional view of the side view from the left of a device according to the invention, the horizontal adjustment process is illustrated by the gray background of individual parts.
  • Fig. La is a front view of section I-I of Fig. 1;
  • FIG. 2 shows a representation corresponding to FIG. 1, the vertical adjustment process being illustrated by the gray background of individual parts;
  • Fig. 2a is a front view of section II-II of Fig. 2;
  • FIGS. 1 and 2 shows a perspective illustration of the view from FIGS. 1 and 2;
  • Fig. 4 is a Fig. 3 corresponding representation from the right.
  • FIG. 1 to 4 show a device for adjusting the mutual position of the soul axes of two barrels of a firearm, not shown.
  • the direction of firing of the firearm is indicated by an arrow 1.
  • This firearm is a combination of a large-caliber self-loading socket and an attached rapid-fire rifle with a common trigger device, the course of which can be adjusted relative to one another should.
  • One barrel, here the barrel of the large-caliber self-loading socket (not shown) is mounted without play in an intermediate sleeve 3, which is firmly connected to the gun housing.
  • the core axis of this barrel is therefore fixed to the housing and coincides with the longitudinal axis 3a of the intermediate sleeve 3 in the present exemplary embodiment.
  • the mounting m of the intermediate sleeve 3 allows a longitudinal movement of this barrel during the shooting process. Nevertheless, for reasons of better readability of the description, this run is referred to below as "stationary run".
  • the position of the other barrel, here the barrel of the add-on rapid-fire rifle (not shown), or its soul axis, is determined by two suspension points: at one of these points, the barrel is easily pivoted, while at the other point it has one eye 7a first actuator 7 is connected.
  • the first actuator 7 can be shifted to the side, ie into or out of the image plane, and the height, ie upwards or downwards.
  • this run is referred to below as a "pivotable run”.
  • the displacement of the first actuator 7 takes place separately to the side and height by rotating a first and a second adjustment eccentric 9 or 11.
  • the adjustment is designed in the present exemplary embodiment so that the first actuator 7 m in each of these directions, starting from the middle position, is displaceable by 1.5 mm. The adjustment process is explained in more detail below with reference to FIGS. 1 and 2.
  • the first adjustment eccentric 9 is cylindrical and is mounted free of play and rotatably on a cylinder 11 ′′ of the second adjustment eccentric 11 around the intermediate sleeve 3. It has a circular eccentric ring 9a, the center of the circle 9e of which lies outside the axis of rotation of the first adjusting eccentric 9 (cf. FIG. 1 a). In the present case, this axis of rotation coincides with the longitudinal axis 3a of the intermediate sleeve 3.
  • the adjustment eccentric 11 comprises a cylinder 11 'and the cylinder 11'', both of which are mounted on the intermediate sleeve 3 without play and rotatably.
  • the two cylinders 11 'and 11'' On the underside of the intermediate sleeve 3, the two cylinders 11 'and 11'', seen in the circumferential direction, engage in one another, so that when the cylinder 11' rotates, the cylinder 11 '' is also rotated.
  • the common axis of rotation of the two cylinders 11 'and 11'' lies on the core axis of the stationary barrel.
  • the cylinder 11 ′′ has a circular eccentric ring 11a, the center of which lies outside the axis of rotation of the second adjusting eccentric 11 (cf. FIG. 2a).
  • the first actuator 7 is connected to a second actuator 17 via a first tongue and groove connection 13 (see FIG. 4). As a result, the first actuator 7 can only be displaced relative to the second actuator 17 along a first adjustment line x.
  • the second actuator 17 is connected via springs 23a and 23b (see FIG. 1) of a second tongue and groove connection 23 (grooves not shown) to the weapon housing, in such a way that the second actuator 17 can only be displaced along a second adjustment line y .
  • Fig. 1 and la illustrate how the first actuator 7 to the side, ie along the first adjustment line x, is displaceable by the first adjustment eccentric 9.
  • the operative connection between the two parts, which are highlighted in gray for illustrative purposes, can be seen in FIG. 1 a: the first actuator 7 has a horseshoe-like shoulder 7c, on the elongated, substantially parallel sections 7d and 7e, in called the following ribs, the eccentric ring 9a rests without play, and exactly along two lines, which are shown in Fig. La as points 8 'and 8''and are referred to below.
  • the points 8 'and 8'' represent the imaginary intersection of the eccentric 9a with a straight line x', which is aligned parallel to the adjustment line x.
  • the eccentric ring 9a When the adjustment eccentric 9 is rotated, the eccentric ring 9a performs a crank-like movement (ie simultaneously to the side and height) around the center of rotation of the adjustment eccentric 9.
  • the periphery of the Eccentric ring 9a stops in the contact points 8 'and 8''without play contact with the first actuator 7.
  • These contact points 8' and 8 '' are at the height of the straight line x '. Since this straight line x 'moves along with the center 9e of the eccentric ring 9a (it can coincide with the adjustment line x), the contact points 8' and 8 '' also shift correspondingly to the height. Otherwise, the eccentric ring 9a does not touch the first actuator 7 during its crank movement.
  • the first actuator 7 when the first adjusting eccentric 9 is rotated, the first actuator 7 is loaded only along the adjustment line x - apart from any frictional forces which occur in the circumferential direction due to the sliding movement of the eccentric ring 9a at the contact points 8 'and 8' '.
  • the first actuator 7 is thereby shifted to the left or right (with reference to FIG. 1 a), depending on whether the first adjustment eccentric 9 is rotated clockwise or counterclockwise from its central starting position shown in FIG. 1 a.
  • the tongue and groove connection 13 with the second actuator 17 ensures that the first actuator 7 does not deviate from the adjustment line x, for example due to the said frictional forces.
  • the ribs 7d and 7e slide up or down relative to the eccentric ring 9a, but remain in contact with it at the height of the straight line x '(the position of the Contact points 8 ', 8' 'on the first actuator 7 are then shifted downwards or upwards accordingly.
  • the length of the ribs 7d, 7e is designed so that the eccentric ring 9a even at maximum high displacement of the first actuator 7 from the ripper. 7d and 7e is encompassed.
  • the eccentric ring 9a Since the eccentric ring 9a is supported only on the ribs 7d and 7e in the radial direction, the semicircular section 7f of the shoulder 7c is not necessary for displacing the first actuator 7. It is only used for support the first actuator 7 on the first adjusting eccentric 9 in the axial direction.
  • Figures 2 and 2a further illustrate the displacement of the first actuator 7 in height, i.e. along the second adjustment line y, by turning the second adjustment eccentric 11 (here too, the parts involved are grayed out).
  • the first actuator 7 is displaced via the second actuator 17, which in turn is in operative connection with the eccentric ring 11a of the cylinder 11 ′′.
  • the functional principle on which the operative connection is based is essentially the same as for the eccentric ring 9a and the first actuator 7.
  • FIG. 2a illustrates this:
  • the eccentric ring 11a lies along two lines, which are designated as contact points 18 'and 18' ', on two ribs 17d or 17e of an oval-shaped shoulder 17c without play.
  • the contact points 18 ', 18' ' are the intersection points of the eccentric ring 11a with a straight line y', which is aligned parallel to the second adjustment straight line y and moves with the center lle of the second eccentric ring 11a.
  • the eccentric ring 11a is in its crank-like movement about the center of rotation of the second adjusting eccentric 11 with the second actuator 17 only at the two contact points 18 ', 18' ', so that the second actuator 17 thereby is loaded in the direction of the second adjustment line y (the semicircular outer sections 17f and 17g of the shoulder 17c are spaced apart from the eccentric ring 11a and only serve to support the second actuator 17 in the axial direction).
  • the direction of movement of the second actuator 17 is guided by the second tongue and groove connection 23.
  • the first tongue and groove connection 13 causes the first actuator 7 to be displaced with the second actuator 17.
  • the displacement of the first actuator 7 along the second adjustment line y (by rotating the second adjustment eccentric 11) thus takes place indirectly via the second actuator 17.
  • the displacement along the first adjustment line x (by rotation of the first adjustment eccentric 9), on the other hand, is a relative movement supply of the first actuator 7 to the second.
  • the actuator 17 thus acts as a kind of cross slide.
  • the adjustment lines x and y are aligned orthogonally to one another. In this way, the position of the first actuator 7 or the eye 7a can be adjusted separately to the height and side.
  • the two adjustment eccentrics 9 and 11 each have a cam 9b and 11b, which fulfill a double function: on the one hand they are handles for manually turning the adjustment eccentrics 9 and 11, on the other hand they serve as bearing shells for receiving locking bolts 21 'or 21' '.
  • the essentially ring-shaped locking disk 25 is connected to the intermediate sleeve 3 via a tongue and groove connection 27 and is thus mounted in a rotationally fixed manner. It has a first stop 25a on one side (see FIG.
  • the locking bolts 21 'and 21'' are spring-loaded in the direction of the locking disc 25, so that when the adjusting eccentrics 9 and 11 are rotated, the cutouts of the locking disc 25 are printed automatically.
  • the millings are slightly ablated on the flanks, so that the adjustment eccentrics 9 and 11 can be turned directly without having to pull the locking bolts 21 'and 21''out of the millings. The force required for this is measured over the strength of the springs so that the adjustment eccentrics 9 and 11 are secured in their position against unwanted misalignment.
  • a moderate spring strength is sufficient for this, since the forces acting on the adjustment eccentrics 9 and 11 during the shooting process from the pivotable barrel via the first actuator 7 are relatively low due to the small lever arm, corresponding to the eccentricity of the eccentric rings 9a and 11a.
  • the lever arm is significantly cheaper, so that an adjustment by hand is easily possible.
  • the adjustment positions of the adjustment eccentrics 9 and 11 are accordingly predetermined by the milled-out of the locking disk 25.
  • the cutouts are arranged in such a way that the first actuator 7 is gradually shifted by a constant value from one engagement position of the locking bolts 21 'and 21' 'to the next when the adjusting eccentrics 9 and 11 are turned.
  • the advantages of the device according to the invention can be seen particularly clearly on the basis of the exemplary embodiment shown here. These are mainly due to the relatively high power consumption with a small footprint.
  • the force absorption capacity can be increased by an axial extension of the contact surfaces between the two eccentric rings 9, 11 and the actuators 7 and 17, respectively, without this requiring excessive space.
  • By appropriately dimensioning the device it is easily possible to adjust modules that are even heavier or more heavily stressed than those mentioned here by way of example and to secure them in their position.
  • a further advantage lies in the possibility of adjusting the second module, namely the core axis of the pivotable barrel, all via the first actuator 7 (or the eye 7a), that is to say via a single suspension point. This is achieved by the cross slide-like mounting of the first actuator 7. This also results in a very compact design, which contributes z ⁇ the space advantages mentioned.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Optics & Photonics (AREA)
  • Aiming, Guidance, Guns With A Light Source, Armor, Camouflage, And Targets (AREA)
  • Thermistors And Varistors (AREA)

Abstract

L'invention concerne un dispositif servant à régler la position relative d'au moins un premier et un second module d'un système d'arme à feu, qui comporte au moins un premier excentrique de réglage (9) rotatif qui est en liaison active avec au moins le premier module, de telle sorte que si l'on tourne le premier excentrique de réglage (9), le premier module peut être, par rapport au second module, déplacé le long d'une première droite de réglage (x) ou basculé à l'intérieur d'un premier plan de réglage.
EP00940253A 1999-05-21 2000-05-16 Dispositif de reglage pour un systeme d'arme a feu Expired - Lifetime EP1179172B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19923474 1999-05-21
DE19923474A DE19923474A1 (de) 1999-05-21 1999-05-21 Justiervorrichtung für ein Schußwaffensystem
PCT/EP2000/004444 WO2000071963A1 (fr) 1999-05-21 2000-05-16 Dispositif de reglage pour un systeme d'arme a feu

Publications (2)

Publication Number Publication Date
EP1179172A1 true EP1179172A1 (fr) 2002-02-13
EP1179172B1 EP1179172B1 (fr) 2006-01-18

Family

ID=7908831

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00940253A Expired - Lifetime EP1179172B1 (fr) 1999-05-21 2000-05-16 Dispositif de reglage pour un systeme d'arme a feu

Country Status (8)

Country Link
US (1) US6701661B2 (fr)
EP (1) EP1179172B1 (fr)
KR (1) KR100539855B1 (fr)
AT (1) ATE316236T1 (fr)
CA (1) CA2374594C (fr)
DE (2) DE19923474A1 (fr)
WO (1) WO2000071963A1 (fr)
ZA (1) ZA200108615B (fr)

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DE19953365A1 (de) * 1999-11-05 2001-05-23 Heckler & Koch Gmbh Verankerungselement für ein Schuzwaffensystem sowie Schußwaffensystem mit einem solchen Verankerungselement
US7726060B1 (en) 2005-02-22 2010-06-01 J. Allen Enterprises, Inc. Firearm fastening assembly and method of use
US8307889B2 (en) 2010-05-13 2012-11-13 Randy Lewkoski Assembly for controlling annuli between tubulars
US9631885B2 (en) 2011-01-13 2017-04-25 J. Allen Enterprises, Inc. Rifle stock assembly for different barreled receivers
WO2013028881A1 (fr) * 2011-08-24 2013-02-28 Tap Tap Tactical Inc. Ensemble de montage du type à rail pour arme à feu pour un positionnement interchangeable rapide des accessoires et son procédé d'utilisation
DE102020006956A1 (de) 2020-11-13 2022-05-19 Damian Hellmann Schnellmontageadapter für eine wiederholgenau reproduzierbare Montage von Nach- und Vorsatzanbauten an Zieloptiken

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US3098410A (en) * 1962-11-26 1963-07-23 Edward M Giza Adjusting mechanism for recoilless rifle spotting barrel
US3228299A (en) * 1963-11-18 1966-01-11 Andrew J Grandy Bias adjustment for spotting rifles
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Also Published As

Publication number Publication date
US6701661B2 (en) 2004-03-09
US20020066361A1 (en) 2002-06-06
ZA200108615B (en) 2002-06-13
ATE316236T1 (de) 2006-02-15
KR20020013552A (ko) 2002-02-20
DE19923474A1 (de) 2000-11-30
CA2374594C (fr) 2006-10-17
DE50012081D1 (de) 2006-04-06
KR100539855B1 (ko) 2005-12-28
WO2000071963A1 (fr) 2000-11-30
EP1179172B1 (fr) 2006-01-18
CA2374594A1 (fr) 2000-11-30

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