FR2670280A1 - AUTOMATIC LIGHT WEAPON. - Google Patents

Abstract

a) Automatic light weapon, in this case rifle. b) A rotatable, rotatable inertia mass has been provided which is coupled to the cylinder head so that the inertia mass rotates constantly during the period of time between the start of a blow and the instant when the weapon is ready to fire the next shot, and releases for at least part of this time the kinetic energy stored to drive the breech. c) Armaments industry.

Description

The automatic light weapon The invention relates to a light weapon

automatic,

  in this case a rifle, equipped in a solid room

  the barrel of a vertical cut relative to the axis of the barrel, wherein a cylinder head substantially cylindrical is disposed coaxially and pivots about its longitudinal axis for feeding, the cylinder head having a chamber aligned with the barrel when the breech

  is in the firing position, and equipped with a

  to tilt the bolt from the firing position to the feed position, the chamber then being accessible for the insertion of a cartridge, and to tilt the bolt into a position

  firing after insertion of the cartridge.

  A weapon of this type is described in German Offenlegungsschrift No. 2,813,633. On this known weapon, the cylinder head constitutes at the same time the Maltese cross wheel of a Maltese cross mechanism and a driving wheel meshes with nipples in the grooves of the Maltese cross wheel The driving wheel itself is driven by a drawer which, moved back and forth and connected to a gas borrowing system, rotates two steps of 1800 each the driving wheel of the Maltese cross mechanism, this wheel returning to stop after each step During the loading process which is performed automatically after the start of a stroke, the cylinder head pivots twice, which also requires- two pivoting of the wheel

  maneuvering This one being stopped before the pivot-

  is braked until it stops between pivoting.

  Since the driving wheel or operating wheel rotates only step by step and is strongly accelerated at the beginning of each step and strongly braked at the end of each step, this presents a significant risk of wear at the level of the wheel. coupling between the drawer and the maneuvering wheel particularly at a high rate or firing frequency which amounts to approximately 2000 rounds

  per minute on automatic weapons, and when

  sequence the average speed of rotation of the operating wheel is high On the other hand, the rate is limited upwards if certain given values must not be exceeded for the acceleration and the braking of the

maneuvering wheel.

  The invention must make it possible to avoid accelerations by jolts on a weapon of the type described at the beginning.

  is solved according to the invention to the extent that it pre-

  sees a rotatable piece drivable and coupled to the cylinder head so that the driven rotating part 3 - constantly rotates after the start of a stroke until

  when the weapon is ready to fire the next shot.

  The weapon is designed so that the mechanism

  to rock the bolt does not require braking to a stop during the time elapsing between the start of a stroke and the moment when the position allowing the firing of the next stroke is reached. However, when the firing position of the next stroke is reached, the entire mechanism

  may be at rest The advantage of

  vention lies in the reduction of solicitations in fits and starts. The rotating part that can be driven can be

  independent training, for example an electro-

  engine or an internal combustion engine in such

  embodiments on which the rotating part can

  If the driving force is stopped when the firing position of the next stroke has been reached, it is possible, depending on the drive used, to switch off or stop, for example, the above-mentioned electric motor, or to disconnect the electric motor or the internal combustion engine and the rotary part driven, for example using a clutch It is also possible to provide a hydraulic clutch which is not disengaged, but which somehow skates when the piece rotary drive is stopped as described above and that the engine continues to rotate It is also conceivable

  to use, instead of a hydraulic clutch, an

  Friction clutch running dry.

  In one embodiment of the invention, it is provided that the rotatable piece which can be driven is a mass of inertia coupled to the yoke so that the mass of inertia releases, at least during a part of

  of the time mentioned above, film energy

  stored tick to drive the breech While

  on the known weapon the maneuver wheel driven direc-

  the drawer must be as light as possible because of the significant acceleration and braking to which it is subjected, must therefore have a mass of inertia as low as possible, it has been provided in this embodiment a mass of inertia that is able to perform mechanical work because of the kinetic energy that it has stored up.

  lies in the fact that due to a more

  the current techniques, the mechanics of

  rocking the number, the number and the violence

  The presence of jolts is reduced and in that due to the regular rotation movement, the mechanism according to the invention is also suitable for high speeds. The mass of inertia can, as in the example of FIG. described below, be constituted by pieces of the weapon However, the mass of inertia may also be entirely constituted

  or partially by the rotor of an engine (an electric motor

  for example an internal combustion engine.

  According to one embodiment of the invention, it is possible to equip the weapon with a conventional piston, brought back

  in initial position after the expansion of

  burstion by a recuperating spring, the energy of this res-

  recovering fate that can help to rotate the cylinder head and possibly also to drive the feeding mechanism Such a spring can be very advantageous for making the movements more regular and therefore obtain

  a more regular speed On another form of execution

  of the invention, it was however provided that in advance

  In the case of a gas-borrowing system, the mass of inertia is driven by the piston essentially uniquely when the gases exert a pressure. The arrangement is therefore provided for the automatic operation of the weapon. Even in the absence of a piston recovery spring, the mass moment of inertia of the mass of inertia and the kinetic energy supplied to the mass of inertia by the piston must be sufficiently large to executing all the movements of the weapon during the return of the piston to the initial position, the return taking place in the present case under the action of the mass of inertia On this embodiment, it

  It is advantageous if, in the presence of a recuperating spring,

  the arrangement is designed so that the weapon remains operational in the event of rupture of the recuperating spring by the energy stored by the mass of inertia; however, in this case, the operating capacity of the weapon may be somewhat limited. In another embodiment of the invention the system

  Borrowing gas is designed without recovery spring.

  In this case, the mass of inertia and the energy supplied to it are therefore provided in such a way that the operating capacity of the weapon is ensured.

  for all intended firing modes in the absence of a

recovering spell.

  An important advantage of the invention, fully highlighted in particular on embodiments without

  recuperative spring, lies in the fact that the movements

  rotating mechanism can be carried out independently

  the presence of springs and that one can choose

  therefore, almost any work speed.

  On the other hand, the arrangements comprising springs are generally operative only over a limited range of working speeds and the working speeds that can be achieved with springs are limited by maximum values since the spring has to be 6 -

  also accelerate his own mass when relaxing.

  The energy stored in the mass of inertia is not only used primarily to tilt the cylinder head

  but it also drives other pieces of the weapon.

  Thus, in one embodiment of the invention, the rotatable piece that can be driven is coupled to a

  cocking lever used to arm the dog with the weapon.

  This makes it possible to obtain a particularly simple construction of the weapon and avoids, as presented later

  in the description, solicitations in fits and starts.

  In one embodiment of the invention, the weapon, as well as the known weapon described at the beginning, presents

  least one orbiform that controls the feeding mechanism

  introduction of magazine cartridges into the

  the breech chamber, it is intended that at least one orbi-

  shape forms an integral part of the rotating part

  be driven, in this case the mass of inertia.

  The advantage of this embodiment, as well as that of other embodiments described later reside in the fact that parts that anyway

  are necessary for the realization of the weapon,

  buoy to the mass of inertia so that the weight of

  the weapon does not increase despite a relative mass of inertia

important.

  The mass of inertia must not be in the form

  of a homogeneous mass and it is possible to

  rotational masses about separate axes, these masses being suitably coupled by means of gears

  For example, on another form of execution of the invention

  However, it has been foreseen that all the parts constituting the mass of inertia revolve around a single common axis. This makes it possible to do without a gear.

  and realize a very compact simple construction.

  In one embodiment of the invention comprising, in a Maltese cross mechanism driving the bolt,

  a maneuvering wheel that performs a complete revolution

  During the time between the start of a stroke and the moment when the bolt returns to the firing position of the next stroke, a locking mechanism has been provided which locks the maneuvering wheel exactly after one complete revolution. Such a locking mechanism seems appropriate when firing shot by blow or blows succeeding quickly or after the last shot of a burst This locking device can provide the mass of inertia a certain amount of energy

  kinetic so that kinetic resistances are unexpectedly

  tense, resulting for example from fouling or

  a change in the lubrication conditions can be reliably overcome. Nevertheless, thanks to the locking mechanism, the weapon is

  well-defined position when the strike is fired.

  Even when this locking mechanism is provided,

  the number of jerk accelerations of the rotating part

  The maximum amount of travel is 50% of the known weapon referred to above.

  is also appropriate in case of gusts or firing

  tinu because he ensures that the movements of the weapon

  only after the detonation of a car-

  touch. In one embodiment of the invention, the piston acts on a crank coupled to the mass of inertia. This construction is particularly simple to produce and is not bulky and makes it possible to reduce, in a simple manner even in the absence of recovery, the piston in the initial position, after the fall of the pressure of 8 - gas, thanks to the mass of inertia Another advantage lies in the fact that the piston does not perform a vacuum stroke at the beginning and the end of its drive movement of the mass of inertia This also increases the allowed rate. The preferred position of the crank in the firing position is a few degrees after the top dead center and the throttle pressure drops at the latest at the moment the crank reaches the bottom dead point. This allows the energy to be transmitted quickly and reliably. of

  piston to the mass of inertia The top dead center corresponds to

  lays in the example of execution approximately with respect to the firing direction at the extreme position

before the piston.

  According to one embodiment of the invention, the lever

  of armament present, pivoting about the pivot axis

  the dog, a lever connected by a conductive rod

  an eccentric articulation of the rotary part

  born, this articulation being the one on which

  the piston The described embodiment is characterized by

  also by a simple construction, not very

brante.

  In one embodiment of the invention, the spring

  -projector is maxed out at the latest at the moment the pressure of the gases drops The advantage here lies in

  the fact that an operation requiring a quantity

  a significant amount of energy, namely the striker spring bandage, is effected directly by the pressure of the gases so that the energy stored in the mass of inertia after the pressure drop of the gases can be less important and therefore the moment of mass inertia of the mass of inertia also that if this stored kinetic energy was also to serve

to bandage the striker spring.

  The embodiment of the invention described by claim 14 has proved to be particularly advantageous from the point of view of the construction and the

  The form of execution described in the

  14 presents a particularly adequate form of control of the feed mechanism that introduces the magazine cartridges into the chamber. -10-

2670280

  The following are described and commented on by means of sketches of embodiments of the invention. The figures show: FIG. 1 is a side view, a partial view, of parts of an automatic rifle which are of interest for the invention, Fig 2 a top view in the direction of arrow II in Fig 1, Fig 3 a front view in the direction of arrow III in Fig 1, Fig 4 a rear view in the direction of the arrow IV in FIG. 2, FIG. 5 is a section along line VV in FIG. 2, FIG. 6 is a section along line VI-VI in FIG. 2, FIG. 7 is a section along line VII-VII in FIG. a section along the line VIII-VIII in Figure 2, rotated 180, Fig 9 a longitudinal section of the cylinder head with cylindrical cylinder head, rotated 180 and thus oriented similarly to Figure 4, Fig 10 a section according to line IX-IX in fig 2, also rotated 180,

  Fig 11 a graphical representation.

  Fig 12 a side view corresponding to FIG 8, all-

  FIG. 13 shows a view of the striker in the direction of the arrow VIII in FIG. 12, partial view, FIG. 14, a detail of an example of modified execution, FIG. 15, a side view of the striker. , Fig 16 a view of the striker in the direction of the arrow XVI in Fig 15 and

  Fig 17 a section along the line XVII-XVII in Fig 15.

  Fig 18 to 20 details of the movable driver and a guide axis of a sliding guide, Fig 21 a

  to f the operating mode of the sliding guide.

  Fig 3 is enlarged with respect to Fig 1 and

fig 4 to 8.

  12 - The representation of FIG. 2 is enlarged by a factor

  1.17 with respect to FIG. 1 and FIGS. 3 to 7.

  The examples of execution represented by the sketches refer to an automatic rifle intended for firing cartridges without a case. As shown in FIG. 9, the integral part 2 of the barrel 1

  has a cylindrical cut 3 whose axis is perpendicular to

  dicular to the axis of the barrel and cut the latter.

  This cutout 3 serves as a housing for a cylindrical yoke 4 which pivots around the axis 3 of the cutout 3.

  sketch, this breech is presented in shooting position.

  In this firing position, a chamber of cartridges 9

  drilled in the cylinder head 4 is aligned with the core 5 of the barrel 1.

  The chamber 9 is symmetrical with respect to a transverse median plane of the rifle, the axis of the barrel 1 being perpendicular to this plane and the axis of the cylinder head 4 contained in this plane. The cartridge without case 14 located in this chamber is constituted a propellant charge 8 and a projectile 7 protruding from the front face The chamber 9 whose passage section is almost square, has on both sides of the mentioned transverse median plane of the bearing surfaces 10

  protruding from the passage section and over-

  which rest the corresponding bearing surfaces 11 of the propellant charge 8, which determines the position of the cartridge 14 in the chamber 9 The cartridge 14 shown

  FIG 9 is based on the two bearing surfaces 10 di-

  opposite and the propellant charge 8 is indented at the left end in FIG 9 at the two other diametrically opposed corners so as to form a housing for the bearing surfaces which are not drawn in Figure 9 and which are intended for a cartridge introduced in

  opposite direction in the chamber, that is to say, the projection of

  tile would be pointing to the right; this does not prevent the cartridge shown in fig 9 from taking the position

described.

-13 2670280

  On the side of the cut-out 3 opposite the barrel 1, a person

  cutter 21 is housed in an insert 23 (FIG. 12) introduced into a hole 22 of the part 2; the longitudinal axis of the striker 21 is aligned with the core of the barrel 1 The striker is provided with the opposite side to the yoke 4 of a shoulder 24 which bears against the bearing surface 25 of the insert 23

  after the ignition of the propelling charge of the car-

  When coming to rest on the bearing surface

  the shoulder 24 creates a seal which prevents

  to a large extent the flue gas to escape.

  Striker 21 is normally in the position shown in Fig 1; in this position, the end striking the primer of the cartridge when fired does not pass through the envelope of the blank 3 And this even when

  the weapon is disarmed and the dog 66 is resting on the

  To cause inflammation of the cartridge, the striker 21 is struck by the dog 66 forwards,

therefore to the left in fig 1.

  After the start of a stroke, the weapon is

  9, by rotation of the yoke 4 of 90 'clockwise (counterclockwise in FIG. 7), so that the chamber 9 is perpendicular to the hole 5 and that one of

  open ends of the chamber is in front of the

  gasin 31 attached to the barrel 1 of the weapon, parallel to it. This magazine 31 is a charger in which the

  cartridges 14 are arranged perpendicular to the direction

  firing point, the tips 33 of the projectiles 7 being oriented towards the axis of the barrel The cartridge 14 in the first position (last position in the firing direction) in the magazine is aligned with the chamber 9 of the cylinder head 4 when it is in the feeding position The piece 2 is provided with a window 12 on the opposite side to the magazine 31 In the other figures, the representation of the cartridges 14 has been simplified The scale of FIG. 9 differs somewhat from that of the other figures, fig 9 itself is not 14 - quite to scale The piece 2 has been removed in some figures or simply sketched by outlines

  to facilitate the reading of the drawings.

  The driving of the bolt 4 is ensured inter alia by a Maltese cross mechanism; this one understand

  the cylindrical yoke face oriented towards the observation

  in FIG 7.4 grooves 35, in particular 4 grooves 35

  arranged radially spaced at an angle of 9 Q O and

clogging on the envelope surface.

  An axis 40 is housed in the part 2 and is located in FIG. 7 at an angle of 45 to the right below the axis 3 'of rotation of the yoke 4 and outside the cutout 3, but contiguous to this one; its axis of rotation is parallel to the axis 3 'of rotation of the yoke 4 Starting from the right end, so on the side facing the observer in FIG. 1, the following parts are fixed integrally to the axis A disk plane 42, fixed and centered on the axis 40 (FIG. 1) behind the disc 42, according to the orientation of FIG. 1, a first orbiform 44, quasi-circular and having only

  that a slight eccentricity with respect to the axis 40, cf fig 5.

  A second quasi-circular orbiform 46 is mounted behind the first orbiform 44, cf FIG. 6, but the point of attachment on the axis 40 has a relatively large eccentricity, namely at mid-distance between the center and the

circumference.

  Behind the second orbiform 46 is a disk 48, clearly visible in FIG. 2 This disk is centered on the axis 40 and has on the rear face two pins 50 and 51 provided for engagement in the grooves 35, cf. FIG. and 7 In the firing position, position shown in all figures, with armed dog restrained by the trigger,

  the pins 50 and 51 are not engaged in the grooves 35.

_ 15 -

  The studs 50 and 51 are equidistant from the axis 40; they are however not diametrically opposed but form an angle of 145 open with respect to the yoke 4; the nipples 50 and 51, however, are equidistant from the axis of rotation of the yoke 4. They are therefore spaced from the end of the nearest grooves 35, oriented downwards and to the right in FIG. provided with the pins 50 and 51 is contiguous and parallel to the side wall of the part 2 The part 2 is crossed by the axis 40 whose end passes through the side wall of the part 2, not visible to the observer in the fig 1

  at the top of fig 2 and pointing towards the observation

  In FIG. 4, from the bottom to the top of FIG. 2, the end of the axle firstly supports a cam disk 54 (FIG. 2) integral with the axle and intended for indirect locking of the bolt. then a

  disc 56 whose circumference forms a trigger cam.

  and a disk 58 fixed and centered on the axis 40 The outer face, visible in FIG. 4, of this disk 58

  a post 59 connected to a control wheel 175 by a

  elastic stretcher 230 formed by a leaf spring This control wheel 175 located on the axis of the disk 58, in front of the latter in FIG. 4, allows the user of the weapon to actuate the disk 58 and thus the 40 by rotating the control wheel 1751 shown in FIG.

  in the opposite direction of clockwise.

  In this case, the control wheel 175 rotates with difficulty so that the axis 40, shown in FIG.

  counterclockwise when operating

  Normally, the cylinder head which will be described later, does not drive the wheel. When this control wheel is easy to rotate, it is driven by the rotational movement of the axis 40 but the torque exerted on the wheel is extremely low. so that the rotation of the control wheel does not present a risk for the shooter in the case of a burst firing for example The control wheel 175

16 ô -

  It is also lockable The parts described above, integral with the axis 40 and the axis 40 itself constitute a mass of energy in rotation or a device similar to a steering wheel which allows to store energy in this mass of inertia and to restore it to perform the loading This mass of inertia allows in particular

  to store a delivered kinetic energy in a relatively short period of time and to restore it for a relatively long period of time.

  The application example relates to a gas-borrowed weapon whose non-visible piston acts on the right end of a connecting rod 60 shown in FIG. 1. Immediately after the start of a blow, the gases exert a pressure to the left on the connecting rod 60 shown in FIG. 1 The connecting rod 60 is fixed to the disc 42 by means of a hinge 61 to which is also coupled a conducting rod 62 In the firing position represented in FIG. 1, this hinge 61 is not in the top dead center but shifted by about 30 in a clockwise direction. Consequently, the action of the connecting rod 60 by the gases inevitably causes the disk 42 to rotate. and the axis 40 as well as all the parts attached thereto, a clockwise rotation on the Fig. 1 The device is designed so that the drive of the connecting rod 60 by the gas be completed before

  the hinge 61 has reached the bottom dead center, that is to say approximately the position in which the connecting rod 60 has reached the end of the rear stroke (relative to the firing direction) As soon as the pressure of the gases falls, the wheel formed by the axis 40 and the parts so-

  The drives are no longer driven by external actuation, but the kinetic energy stored in the steering wheel continues to rotate clockwise in FIG. 1, at least until 17 - articulation 61 returns for the first time in the

position shown in fig 1.

  The free end of the long lever arm of a dog cocking lever 65 is connected to the hinge 645 of the conductive rod 62, the other end of which is the hinge 61 The cocking lever 65 serves to rearm after the percussion the dog 66 of the weapon, shown in the armed position in FIG 1 During the percussion, the dog moves in the clockwise direction of a watch, in FIG. by pivoting in the opposite direction of the hands of a

  shows by overcoming the resistance of a striker spring 67 in the form of a spiral spring When the weapon is in the firing position, the dog is

  held by the stop hook 68 of a trigger 70 pivoting about a threaded axis 69 secured to the barrel The hook

  The trigger 70 is then engaged by a hinge 73 to a detent rod 74 which, when moved forward, disengages the catch hook downwardly. 68 of the detent 72 and thus releases the percussion of the dog 66.

  The weapon, in so far as it is shown, is only intended for continuous shooting. Burst firing is interrupted when the detent rod 74 is again moved rearward, the dog 66 being then again It is self-evident that it may be appropriate to design a weapon intended for shot-by-shot or short bursts of a determined number of hits; Such measurements are known and do not relate to the present invention. The connection between the trigger bar 74 and the actuated trigger tail

  by the shooter is not represented here.

  The dog cocking lever 65 is mounted on an axle

  75 threaded parallel to the axis 40 and fixed on the piece 2.35 This threaded shaft 75 also serves as pivot dog 66.

  18 - The cocking lever 65 is essentially formed by a plate stirrup whose branches 265 and 267 are connected by a back 270 visible in section on the partial view of FIG. 1. The branch 267 is contiguous with the branch 78 of the dog 66 and has two cutouts 272 in the shape of a ring segment, symmetrical with respect to

  to the axis and in which are engaged two posts 274 located on the branch 78 of the dog 66.

  The angle of the circumferential tenons 274 is smaller than the angle formed by the cuts 272, this angle being about 9 O greater than the width of the posts 274, measured in degrees. The angle formed by the cuts 272 is therefore sufficient. large so that the edges of these cutouts do not come into contact with the tenons of the le-15 dog arming 65 when the cocking lever returns, after arming the dog, in the position shown in FIG. 1 and that the percussion of the dog 66 is triggered The arming of the dog 66, by overcoming the

  resistance of the striker spring 67, begins when, for example,

  both of the position shown in FIG. 1, the disc 42 has traveled only a few degrees of angle and that, as

  as shown in FIG. 11, the disk 42 is still in the acceleration phase. The flywheel will therefore not undergo a sudden shock transmitted by the conducting rod 62. The braking force exerted by the mass of inertia, during the acceleration, on the connecting rod 60 reduced in a certain

  This reduces the amount of stress that occurs in a jerk.

  In the example of execution considered, the pressure drop coincides with the coincidence of the moment when the dog 66 is armed At this moment, the cylinder head 4 shown in FIG. 7 has already rotated 900 in the direction of the The energy required for this rotational movement of the cylinder head 4 is still provided directly by the pressure that the gases exert on the connecting rod 60. The movements that the dog 66 will still have to perform after completion. arming until the weapon is in the firing position again or, in the case of a continuous fire,

  until the next shot can be triggered automatically, are performed only with the kinetic energy accumulated in the flywheel 10 after the drop in gas pressure.

  The posterior end of the rod 60 formed by a sheet is provided with a heel 80, oriented obliquely towards the front and the bottom, this heel 80 contiguous to the hinge 61 comes into contact with the heel 81 of a stop lever 82 just before the disc 42 reaches the position shown in Fig 1 The heel 80 therefore rotates the stop lever 82 shown in Fig 1 counterclockwise by overcoming the resistance of a spiral spring 83 so that the long lever arm 84 of the stop lever 82 intercepts the stroke of a stop 85 on the connecting rod 60. This stop which is not undercuts blocks the movement of the rod to the left and interrupts the rotation of the flywheel As soon as the movement to the left of the connecting rod 60 has been stopped and therefore the long lever arm 84 is no longer subjected to effort, the stop lever 82 is brought back by the spiral spring 83 into the position representing e in Fig 1 and the weapon is then

  again ready to deliver the next shot.

  The stop lever 82 pivots about an articulation axis 86 fixed on the part 2 This hinge pin 86 supports

  also a first 88 pivoting control plate equal to

  1 located immediately behind the stop lever 82, see also FIG. 5. This control plate 88 has a large cutout 89 in the form of

  hook, the distance between the two parallel surfaces 90 and 91 of this cutout being equal to the diameter of the first orbiform 44.

  44, the first control plate 88 thus pivots slightly about the hinge pin 86. A second control plate 95, located in FIGS. 1 and 5 immediately behind the first control plate 88, is mounted on a pivot 93 fixed above the hinge axis 8610 and slightly offset in the direction of fire to the left This second control panel 95 has a relatively short oblong cut 96 with two parallel sides 97 and 98 slightly inclined towards the The second orbiform 96, whose diameter is equal to the distance between the sides 97 and 98, is situated in this cutout. The rear end 94 of the second control plate 95 is fixed with the aid of FIG. A pivot 100 approximately in the mid-zone of a bent lever 99 A conductive rod 102 is attached to the lower end of the bent lever 99 by a hinge 101. The other end of the bent lug 99 a conductive rod 102 pivots on a threaded axis 103 secured to the part 2 The position of the hinge pin 103 is slightly less than that of the hinge axis 101 The conductive rod 102 is bent upwards to leave enough space on the dog cocking lever 65 When rotating the two

  orbiforms 44 and 46, the front portion of the free upper end 105 of the elbow lever 99 executes a link movement whose trajectory corresponds approximately to the curve 106 shown in FIG. 6 when executing such a movement , the end 105 of the elbow lever 99

  a cartridge of the magazine 31 in the chamber which is at this moment in a position offset 900 from the representation of FIG. 9.

  If the weapon is to be equipped with a counter of blows for the firing of gusts of three blows for example, it will be possible to mount 21 -

  a control wheel 108 with three teeth on the axis of ar-

  This control wheel 108 will then be driven by a lug 109 fixed on the second control panel 95 and will advance one step each upward movement of the second control panel 95. As has already been the case mentionned,

  this counting device is not the subject of this invention.

  As can be seen in FIG. 7, the axis 40 starting from the position shown in FIG. 1 first rotates 150 clockwise until the stud 50 is engages the downwardly directed groove 35 and causes the counterclockwise movement of the bolt 4 to rotate. After an additional pivoting of 900 of the axle 40, the rotational movement of the bolt The cylinder head is completed and the stud 50 leaves the groove now pointing forwards. When the axle 40 still rotates about 1200, the pin 51 engages in the downward groove 20 and after a further 90 rotation of the bolt has again switched from 900 after a new rotation of the axis

  of about 150, the pins 50 and 51 have taken the position shown in Fig. 7 When the axis 40 performs a complete revolution, the cylinder head 4 rotates 90 times in the counterclockwise direction. rotation of 900, the longitudinal axis of chamber 9 is

  tical and aligned with the first cartridge 7, 8 of the magazine, that is to say that which is at the rear end in the direction of firing Thanks to the movement, described above, of the end 105 of the elbow lever 99, the cartridge is fully engaged in the chamber.

  the yoke 4 latches, as described above, a second time of 90 so that the cartridge which has just been engaged is in the firing position. On the visible side in FIG. 8, the yoke 4 has four recesses. 112 practiced from outside to

  on the circumference of the base of the cylinder.

  22 - The upper end 113 of a stop lever 114 with two biases pivoting about an axis 115 is maintained in the: n of the recesses 112, the notch 112, since o the end The lower free end 116 of the stop lever 114 returns to the position shown on a cam 117 of the cam disk 54. The cam disk 54 is provided with

  11 cam diametrically opposed to the cam 117, the cam 118 having a peripheral angle greater than that of the heart 117 between the two cams 117 and 118, cons-

  equal circular cylindrical surfaces, there are transition surfaces 119 and 120 of radius

  When the end 116 rests on these transition surfaces 119 or 120 during the rotation of the cam disk 54, the pins 50 or 51 are engaged in the rears.

  The notches 112 are approximately in the shape of a relatively open "V" whose two branches form an angle slightly greater than 90. At the tip, the notch has a concave flare. at the outer ends, a convex curvature The stop lever 114 is approximately

  the shape of a "C" The shape of the notches 112 and over-

  transition faces 119 and 120 was chosen such that the lever Stop 114 releases or not the rotation of the cylinder head

  4 without there being an important game at both ends.

  The moments transmitted to the lever arm 116 by the cam disc 54 during its rotation tend to raise the lever arm 116 of the cam disc. Moreover, the moments passed to the lever arm 113 by the yoke 4 during its rota: These tend to lift the lever arm 113 of the bolt 4 to keep the wear at a reduced level. As long as the end 116 of the stop lever is in contact with the cams 117 or 118, the bolt 4 is As soon as the trailing surface 116 contacts the end 116, the cylinder head 4 is driven by the engagement of the stud 50 in the adjacent groove 35 and the groove. end 113 is disengaged from the notch 112 As soon as the cylinder head 4 approaches the feed position, the end 113 of the stop lever 114 is again engaged in one of the notches 112 via of the transition surface 120 of the cam disk 54 After the loading, the pin 51 enters into contact with the groove 35 and tilts the bolt 4

  in the firing position, the cylinder head having turned 1800 with respect to the representation of FIG.

  As can be seen in FIG. 8, a spiral spring 124 acts on a lever with an arm 126 which, fastened to the end

  21 of the firing pin 21 pulls it backwards When the dog 66 is triggered, the latter pivoting in FIG. 8 counterclockwise, the back 76 of the dog essentially constituted by a stirrup strikes. the outer end 130 of the striker 21.

  On the visible side in FIG. 10 of the piece 2 is a ratchet lever 135 mounted on a threaded pin 73. This ratchet lever 137 carries at the adjacent end of the dog 66 a pawl 137 which remains engaged in a surface of FIG. support 138 of the dog as the cam 142 of the disk 56 exerts a radial pressure, outwardly relative to the axis 40, on the end 140 of the ratchet lever 135 whose other end is the ratchet 137 disc 126 has two cam sectors 142 ', 142 "in the form of an arc of a different radius, a progressive transition 143 between the two sections of different radius and a recess 144 inwards which allows the ratchet lever 135 to pivoting in the clockwise direction when the axis 40 performs, after the start of a stroke, the rotation described above and is returned to the position shown in Fig. 1. striker exerts an effort on the dog 66, this one exercises pressure on the opposing notch faces 137 '355 (on the pawl) and 138 which are not self-locking. The dog 66 disengages itself from the ratchet lever 135 and strikes, 24 - insofar as it is not retained by the catch hook 68, the striker 21 triggering the next stroke. The face 66 'of the dog 66 which forms a circular cylindrical surface segment and extends the surface 138 138, then slides along the face 137 '' of the ratchet

  137 and exerts on it a moment that tends to lift the pawl 137 of the face 66 '.

  As shown in FIG. 4, a one-arm lever 152 is

* attached to an axis 150 parallel to the axis 40 This lever 15210 is oriented upwards and connected by a pivot 155 to a conductive rod 154 at the other end of the rod con-

  154 When the magazine 31 still contains at least one cartridge, the latter holds the ejector 158 at a position, relative to the firing direction, behind the next The ejector then rests on a bearing surface 2 'of the workpiece 2. The ejector 158 has above the hinge 56 a curved extension 158' which engages a guide hole 159 '' delimited by blocks 159 and 159 'While lever 152 is attached to the non-visible end for the observer in FIG. 4 of axis 150, lever 152 being integral with the axis the other end of the axis 150, visible to the observer, 25 carries a lever to an arm 160, integral with the axis Ce lever 160 has at its end an oblong hole 164 in

  which engages an axis 162 of a lever with two arms 166.

  One of the lever arms of this two-armed lever 166 is defined by the axis 162 and the threaded axis 168. The other lever arm 170 forms an angle of about 1350 with respect to the first lever arm L '. free end of the lever arm 170 has on the face not visible to the observer a pin 172 When a cartridge is in? 5 - the magazine 31, the lever mechanism 158, 154, 152, 166 takes the position shown in FIG. 4, the stud 172 of the lever arm 170 then being situated close to the periphery of the disc 58, without entering into If, on the other hand, the magazine 131 does not contain a cartridge, the lever mechanism 158, 154, 152, 160, 166, the elements 152 and 160 of which are secured to one another, rests through the stud 172 on the circumference of the disc 58 due to the force exerted by a tension spring 171 The stud 172 engages a groove 173 of the disc 58 as a result of the force exerted by the traction spring 171 only when the disc 58 rotates slowly, as is the case when manually actuating the control wheel 175 The curvilinear pattern of the groove 173 finally controls, via the stud 172 and the mechanism lever, the movement of the ejector 158 and takes, in a first time, the position of the cartridge 14 shown in Fig 4; in other words, the ejector 158 rotates clockwise due to the engagement of the extension 158 'in the guide hole 159' '

  and as a result of the movement of the hinge 156 under the effect of the spring 171, so that it is approximately at the location of the cartridge 14 shown in fig 4.

  When the rotational movement of the disc 58 continues and as long as the stud 172 is guided in the first part of the groove 173, the ejector 158 passes through the chamber 9 into the feeding position - the extension 158 'no longer being in the guide hole 159 '' from which it has been released. This has the effect of ejecting the cartridge that may be in the chamber. The second part of the groove 173 has the effect of removing the ejector 158 from the chamber. When the pin 172 leaves the groove 173, 26 - the lever mechanism returns to its initial position and the spring force 71 is exerted again, as mentioned above, on the edge of the disk 58. ejection, a song 152 'of the lever 152 rests on a shank 154' of the conductive rod 154 These edges limit the pivot angle between these two parts.

about 15.

  The automatic rotation of the disk 58 driven by the start of a stroke is performed at an angular speed éle-1 (vée so that the stud 172 does not engage in the groove 173 due to the inertia of the lever to two arms

  166; this prevents the ejector 158 from automatically entering into action when the magazine has been emptied.

  The groove 173 constitutes a mechanical drive and

  Therefore reliable ejector 158 in both directions of ejector action The layout of the groove 173, represented in FIG.

  4, is formed by two successive curved segments. The point where the two segments meet at an open angle constitutes the point of the groove 173 closest to the axis of the disk 58.

  The reset using the control wheel 175 is also necessary when a cartridge has not been fired. During rearming, the axis 40 and all

  coupled parts are turned manually, exactly as it is done, automatically, after the start of a stroke. If the magazine still contains a cartridge,

  key, at the location indicated in FIG. 4, during the reset, this cartridge is engaged, during the rearming of the weapon, in the chamber 9 by the feed mechanism 30 105 when the cylinder head 4 has rotated by 900 compared to the 27 - position it held at the time the shot did not go The new cartridge introduced, the point of the projectile rests, in this case, on the tip of the projectile of the cartridge which has not not fired, release the cartridge that was not fired from the chamber down and eject it by

  the window 12 (FIG. 9). If the magazine no longer contains a cartridge, the cartridge which has not been fired is ejected by the ejector 158.

  FIG. 11 shows a graphical representation of the correlation between the different angular positions of the axis 40 and its angular velocity. The angular position OO on the graph of FIG. 11 corresponds to the position "firing state" of the weapon represented on FIG. the sketches La

  angular position is measured in the clockwise direction in FIG. 1 at an angular position of

  40, the axis 40 and thus the mass of inertia reached the maximum rotation speed of about 250 / ms, which corresponds to a rotation speed of about 69 rpm equivalent to about 4167 rpm. maximum rotational speed is thus twice as high as the rotational speed resulting from a firing rate of 2,000 rounds per minute, assuming the axis 40 rotates

  at a constant speed without stopping between the

  A relatively large fall in the speed of rotation of the mass of inertia takes place between

  this maximum value at an angular position of about 40 and an angular position of about 70 This results from a loss of energy during the first rotation.

  The yoke 4 which rotates easily in the cut-out 3, but nevertheless is well fitted and consequently provides a good seal, in turn transmits, at the end of its rotational movement of 900 mm. kinetic energy to the mass of inertia so

_ 28 -

  that the speed of rotation of the axis 40 increases again

  Between the angular positions of approximately 70 and 9 OW, there is then a gradual decline in the rotational speed, interrupted at an angular position of approximately 2800 by a greater momentary drop in the speed of rotation resulting from the second rotator. 9 OO of the yoke 4 driven by the Maltese cross mechanism Between 100 and 2400, there is also a fall in the speed of rotation due to the energy loss of the mass of inertia following the enaagement The residual kinetic energy at an angular position of 3600, corresponding to an angular speed of the mass of inertia of approximately 10 '/ ms, is destroyed. by the braking of the connecting rod 60 by the stop lever 84. Such a surplus of energy at the end of complete rotation is

  useful for overcoming greater kinetic resistance of the mechanism when it is for example worn or fouled.

  However, to avoid such fouling, the receiver and the mechanism of supply of the weapon

  and the store are sealed, essentially outward.

  Only fig 3 indicates that the pieces of the weapon represented

  on the sketch are inside a fairing 180 in which is also housed the control wheel 175.

  Most of the various disks and levers of the described exemplary embodiment are made of 1 mm thick sheet steel in most cases. In order to be able to make reliable articulated joints with such relatively thin sheets, these assemblies are frequently obtained by folding one of the sheet metal parts around the other piece of sheet metal connected by the joint This is particularly well highlighted by the example of the stop lever 82 when comparing the figs 1 and 5 The horizontal side, pointing downwards in FIG. 1, of this stop lever 82 is extended by a staple folded towards the rear and again upwards around the end of the first sheet metal. -

  Mande 88 in which is housed the axis of articulation.

  This clip which is part of the stop lever 82 indicated by 82 'in FIG. 5 When other staples are visible in the drawing, they are marked by a reference mark

modified accordingly.

  In the exemplary application, the disc 42 has a diameter of about 50 mm, the first orbiform 44 has almost the shape

  of a disk about 41 mm in diameter, the second orbital

  form 46 eccentric to a diameter of about 25 mm, the disc 48 has a diameter of about 38 mm, the disc 56 has a diameter of about 35 mm and the disc 58 has a diameter of about 69 mm The mentioned parts above are part of the mass of inertia At mass moment of mass of these parts, is added the mass moment of inertia of the cam disk 54, the axis 40 and also the pins and the moment. The mass inertia amounts to a total of about 4 x 10-4 kgm 2. At the mentioned maximum rotation speed of about 4100 rpm, the mass of inertia has stored an energy of about 30 J.

  energy is sufficient to perform the movements de-

  previously written without the aid of the piston.

  The dog 66 (FIG. 12) pivots about an axis 75 housed in the piece 2. A striker spring 67, constituted by a spiral spring, is tensioned, which is not represented here, by an automatic cocking device. tear

  after the start of a stroke The dog 66 is essentially

  by a stirrup It has two branches 68

  spaced parallel, joined by a back 69, the spring-

  -pergeter 67 located between these two branches 68 The 29 - - front face of the back 76 is somewhat set back from the front face of the branches 68 These faces of

  branches 68 form a percussion surface 77.

  FIG. 12 shows the position of the various pieces when the weapon is armed. The pawl 137, interacting with a bearing surface 138 of the dog 66, releases when the weapon is in automatic mode the dog 66 each time a new cartridge is introduced into the chamber

  and that the bolt 4 has returned to the firing position.

  The force of a spiral spring 124 intended to pull the percussion

  rearwardly applies indirectly to the end of the striker 21 This spring is mounted on an axis 125 fixed to the part 2 The axis 125 also serves as a pivot to a lever

  to an arm 126, consisting of a slightly bent sheet metal pre-

  sensing an oblong hole through which the lever engages in recesses 128 'provided on two opposite sides of the rod 128 of the striker 21 The recesses 128' are limited in the posterior part of the rod 128, that is to say right on fig 12, by a thickening 127 of the

  rod forming a shoulder 127 'on which come

  puyer the edges of the oblong hole 140 and therefore the lever 126.

  * The piece 127 and the striker are made in one piece and are therefore very robust Despite the proximity of the shutter formed by the shoulder 24 and the corresponding bearing surface, the spring 124 is not in the trajectory flue gas exhaust

  and is therefore little subject to fouling.

  When the dog 66 is triggered, it will then pivot in FIG. 12 in the counterclockwise direction of a dog.

  shows, the front face of the back 76 of the dog 66 hits the end 130 of the firing pin 21 and actuates the firing pin

  amount of force exerted by the spring 124 After 31 - continuing its stroke of about 1 mm, the abutment surface

  77 of the dog 66 hits a stop 129 which bounces the dog 66 due to a certain elasticity of the

  which constitute the dog 66, before the percutter 21 has reached the beginning of the cartridge From the moment the dog has struck the stopper 129, the striker 21 is in free stroke and detonated the cartridge after a certain delay determined by the length of its free stroke and its speed The pro-pulsing gases that develop repress the striker with a great power but it can no longer reach the dog having bounced on the stop The striker, in particular its shoulder, comes to rest on the intended bearing surface of the insert 23 and constitutes a shutter 15 preventing the propulsive gases from escaping, well before the lever 126 has been brought back by the spring 124 in the initial position shown in Fig 12 Before the sealing is done, the gases having exceeded the striker during the detonation escape and present a risk of fouling or destruction of functional parts located derr In order that this rapid retraction movement of the firing pin 21 does not damage the lever 126, the length of the recesses 128 'parallel to the direction of movement of the firing pin 21 has been generously sized. The surface limiting the recesses 128' , on the left on fig 12, is located on the left

  the right face of the stop 129 in FIG 12 The stop 129 is formed by a nut holding the insert 23 in the room 2.

  If the firing pin 21 collapses empty in the absence of a cartridge, the lever 126 attacked by the piece 127 of the percussion

  21 restricts the movement of the striker to the left in FIG 12 by coming to rest on the stop 129.

  32 - The dog 66 having rebounded as a result of the impact on

  the stop 129 by overcoming the resistance of the spring-

  -drawer 67 is again powered by the spring-

  after having reached the point of recoil of its movement, towards the firing pin 21 which has

  time its initial position, the dog 66 no longer reaches the firing pin 21 because

  the dog 66 was intercepted by the weapon

  the dog, meanwhile, in action, and is

  brought back into the armed position shown in fig 12.

  Fig 14 shows a modified version on which the lever 126 and the spring 124 have been replaced by a single leaf spring 150 having as the lever 126 the oblong hole 140 The leaf spring 150 is fixed

by screws 152 on the part 2.

  Figures 15, 16 and 17 show the striker 21, the recesses 128 'being clearly visible The striker 21 has a total length of 22 mm, the rod 128 has a square section of 3.2 mm side over most of its length At the recesses 128 ', the thickness of the rod visible in FIG. 16 is somewhat reduced and comprises at this point 2.8 mm. The piece 127 has on the section of FIG.

  the maximum dimension is 4 mm The posterior face of the per-

  , cutter is a spherical surface area, the shoulder-

  127 'are convex, as shown in FIG.

  The length of the recesses 128 'is 6.5 mm and the maximum length of the workpiece 127 is 2.5 mm. For other dimensions of the striker refer to fig 15

and 17 drawn to scale.

  The diameter of the cylinder head 4 is 34 mm For others

  dimensions refer to Fig 12 drawn to scale.

  33 - The stop 129 and the dog 66 are made of alloy steel

  16 Mn Cr 5 and have a Vickers hardness of HV 1 660 + 60.

  The control wheel 175 is housed in a sleeve 220 welded to the fairing 180 (FIG. 3). The control wheel 175 is held by a screw 222 which engages in the tapped hole 224 of a wheel 226. the adjacent face of the fairing 180 an end of axis 228 in which has been drilled the tapped hole 224, which engages in the hole of the bushing 220 When the weapon is in the firing condition, but not actuated, the axis of rotation of the control wheel 175 and the wheel 226 is aligned with

the axis 3 'of the cylinder head 4.

  FIG. 18 shows the wheel 226 seen from the right in FIG. 3, but turned with respect to the representation of FIG. 3. FIG. 19 is a section along line XIX-XIX in FIG. the direction of arrow 20 in FIG 18 As shown in Figs 18 and 19, the wheel 226 carries, eccentric to its axis of rotation, a spring driver 230 formed by the free end of a leaf spring 300 is fixed to the wheel 226 by a rivet 302 The driver 230 protrudes through the cutout 304 on the face 306 of the wheel 226 The driver 230 is prestressed by the leaf spring 300 towards the disk 58 located at interior of the fairing 180 near the wheel 226 and in the

  same axis as this one when the weapon is not activated.

  If the arming mechanism is to be operated when a shot has not gone or to unload the weapon, the shooter will turn the control wheel 175 by hand so

  that the direction of rotation of the control wheel 175

  rope in the normal direction of rotation of the disc 58

  neur 230 will attack the face 238 of the tenon 59, the face 238 being approximately perpendicular to the plane of the

  fig 4, and will rotate the disk 58 causing the operation

armament described above.

  34 - If, on the other hand, the movement of the parts of the weapon was triggered by the weapon, after the departure of a blow by

  example, this movement should not be transmitted to the

  As described below, the mechanism of the weapon is movable inside the fairing, which prevents, when the weapon is operating normally, the post 59 does not come into contact with the trainer. However, it is conceivable that uncontrolled influences disrupt the operating part of the cocking mechanism and the pin 59 impacts the driver 230 during automatic loading. In this case, the wedge-shaped face 235 pin 65 comes into contact with the driver 230 and pushes it into its housing without

  exert a sensitive couple on the control wheel.

  The tenon 59 has a second inclined slant 240, assuming that the disc 59 rests horizontally, of the

  right to the left in fig 4, so in the direc-

  This bevel 240 must have been provided, since the weapon shown is a gun with a movable mechanism on the carriage. The barrel 1 and the piece 2 integral with the barrel.

  as well as all the other pieces represented are

  bile and guided inside the fairing 180; the guide is perpendicular to the plane of FIG 3 and therefore parallel to the longitudinal axis of the barrel The fairing 180 is equipped for this purpose with guide rails, namely

  protrusions 250 in the form of rods directed

  These guides engage in longitudinal grooves

  dinales 252 which are parallel to the guides and made in the piece 2 secured to the barrel A spring which is not shown, bears on the piece 2 secured to the barrel in the fairing 180 After the start of a stroke, the piece 2 integral with the gun moves backwards with respect to the firing direction as a result of the recoil and

  is repressed, the blow being gone, by the men-

  When this translation towards the rear of the piece 2 secured to the barrel, the disc 58 and the axis 40 aligned with the axis of the disc 58, also move and are therefore no longer aligned with the control wheel 175 secured to the fairing It is therefore possible that for some reason, the control wheel 175 is rotated a little while the piece 2 secured to the barrel is not in the position of rest but shifted to the rear after a shot The coach 230 could then be on the race that the stud 59 performs during the

  forward movement of the integral part of the barrel.

  The bevel 240 has therefore been provided in order to avoid any disturbance That is to say that in the case of the described movement of the pin 59, the bevel 240 comes into contact with the driver 230 and pushes it back into its housing by overcoming the pressure of the spring 300 so as to allow the return of the piece 2 integral with the

  gun in the position assigned to it.

  In order to ensure that the cylinder head 4 which is in position

  firing, return exactly in the same position.

  after the wheel is armed with the control wheel and the shooter does not involuntarily turn the control wheel in the opposite direction, a slide

  was planned on an angle of 3600 between the wheel of com

  Mande 175 and a part integral with the fairing The slide, whose operation is shown in detail in FIG. 21, has been provided on a part 320 enveloping the

  bushing 220 like a flange The slide 330 pre-

  sits an inner edge 332 and an outer edge 334, see also fig 3 The wheel 226 integrally assembled to the control wheel, and in particular the disc 306 door, eccentric with respect to the axis of rotation of the wheel 226,

  an axis 340 which serves as a support for a conducting arm 342.

  This conducting arm 342 has at its end a guide pin 344 led by the edges 332 and 334 of the 36 -

  slide The driver arm 342 is subject to the pres-

  The driver arm 342 and its attachment are clearly visible in FIGS. 18 to 20 in order to be able to better represent the guide pin in the FIG. 3

the axis 340 has been shifted by 1220.

  In the initial position shown in Fig. 21a, position-in which the chamber is aligned with the axis of the barrel, the control wheel 175 is locked by the engagement of the guide pin 344 in a recess 348 of the inner edge 332 this is a ratchet with limit load When the control wheel 175 is turned by the shooter in the right direction, the axis 340 then turning with the disk 306 in the opposite direction of the needles a watch in Fig. 21, the guide pin 344 disengages from the recess 348 and arrives at the position shown in Fig. 21b. When the control wheel 175 is turned in a continuous movement, the guide pin 344 is driven by an oriented surface. outward 354 from the inner edge of the slide outwardly and finally reaches a stop 349 oriented radially inwardly. This stop which is formed by the outer edge 334 of the slide,

  blocks the rotational movement of the control wheel.

  The abutment or surface portion 349 does not exactly follow

  the shape of a ray but has a con

  cellar whose radius of curvature is less than the radius of pivoting of the guide pin 344 about the axis 340 Therefore, the inner end 356 of the stop 349 prevents the guide pin 344 from tilting inwards under the action However, as soon as the shooter releases the control wheel, the wheel 226 can turn back a fraction of a degree of angle, this rotation being generated by the spring 346, and the pin 37 - guide 344 returns to the initial position shown in Fig. 21a by effecting a radial inward movement which releases it from the constricted passage 350 between

  the inner and outer edges of the slide

  try to turn the control wheel 175 into the

  opposite direction, guide pin 344 will move slightly

  in the recess 348 but will abut against a bearing surface 352 of the inner edge 332, as shown in FIG. 21, which effectively prevents rotation of the

  control wheel in the wrong direction.

  The inner edge 332 constitutes in the example of application

  the "first sliding edge" of the claims.

  But the device can also be designed so that the spring 346 presses the guide pin against the outer slide edge and that the stop blocking the rotational movement is located on the outer slide edge. The slide edge pattern must then be modified. accordingly The centrifugal force acting on the guide pin due to the rotation of the wheel

  226 matters little in view of the low speeds

  The described slide can also be used for other rotary mechanisms of a

  weapon and for any rotating mechanism in general.

  This slide lies in its reliable operation and in the fact that the rotation is blocked by a clearly perceived stop after a predetermined angle of rotation, 360 in the example under consideration. After a brief relaxation or reduction of the torque exerted on the workpiece. maneuver, it is possible to perform a

new rotation movement.

  On this weapon, it is possible, thanks to the use of a simple mechanism, to use another slide track to block the rotational movement after an angle of 1800 On such a slide, the projections, facing the inside and outside, edges 332 38 - and 334 are provided twice circumferentially The rotation can also be stopped by the slide

  after an angle less than 1800 It is also pos-

  However, not without restriction on the weapon described, block the rotation at unequal angles, forming a total 360. The protrusions of the edges 332 and 334 will therefore be provided twice and arranged so that the

  movement is blocked after angles of rotation

  tation of 160 and 2000 for example.

  The marks in the claims do not constitute

  restriction but are intended to facilitate the

gripping.

Claims (9)

claims   1 automatic light weapon, in this case a rifle, provided in a piece integral with the barrel (2) with a vertical cutout (3) with respect to the axis of the barrel, in which the bolt (4) essentially of cylindrical shape is disposed coaxially and   rotates about its longitudinal axis for the food   said cylinder head having a chamber (9) aligned with the barrel (1) when the cylinder head is in the firing position, and provided with a mechanism (35, 50, 51) for tilting the cylinder head from the position of shooting at the feeding position,   the room being then accessible for the introduc-   cartridge (14), and to switch   the breech in a firing position after introduction   of the cartridge, characterized in that a rotatable part which can be driven (inertia mass 40, 42, 44, 46, 48, 54, 56, 58) is provided which is coupled to the cylinder head (4 ) of such   so that the driven rotating part rotates   during the period of time between the start of a stroke and the moment the weapon   is ready to take the next shot.   Weapon according to Claim 1, characterized in that the rotatable piece which can be driven is a mass of inertia (40, 42, 44, 46, 48, 54, 56, 58) which is coupled to the yoke (4) so that the mass of inertia releases for at least part of the time period mentioned the kinetic energy   stored to drive the breech.   -40 - 3 weapon according to claim 2, characterized in that it was designed with a gas borrowing system provided with a piston and a recovery spring. 4 A weapon according to claim 2, designed with a   a gas-borrowing system with a piston, which is   characterized in that the mass of inertia (40,42, 44, 46, 48, 54, 56, 58) is essentially driven by the piston (connecting rod 60) only in the presence of the pressure of the gases.   Weapon according to claim 4, characterized in that the gas borrowing system is designed without recovery spring.   Weapon according to one of the preceding claims,   characterized in that the rotating part can   being driven (disc 42) is coupled to an arming lever (65) for arming the dog (66) of the weapon.   Weapon according to one of the preceding claims,   equipped for the insertion of a cartridge into a chamber in the supply position with a feed mechanism (105) which is actuated   by at least one orbiform mounted on an axis, characterized   in that at least one orbiform (44, 46) is an integral part of the rotating part to be trained.   8 A weapon according to one of claims 2 to 7, characterized   rised by the fact that all the parts (40, 42, 44, 46, 48, 54, 56, 58) of the mass of inertia turn around a single common axis. -41 -   Weapon according to one of the preceding claims,   presenting, within a cross mechanism of   Malta driving the breech (4) a wheel of   a workpiece (48, 50, 51) which performs a complete revolution during the lapse of time between the start of a stroke and the moment when the firing position of the next stroke is reached, characterized in that a locking mechanism (stop lever 82, heel 80, abutment surface 85) is provided to stop the operating wheel exactly after a complete turn.   Weapon according to at least one of claims 3   to 5, characterized in that the piston acts on a crank (articulation 61) coupled to the mass of inertia.   11 weapon according to claim 10, characterized in that the position of the crank in the firing position is a few degrees after the top dead center and the fact that the gas borrowing system is designed so that the pressure no later than the moment the crank reaches low dead point.   12 at least weapon according to claim 6, characterized in that a lever serving as a cocking lever (65) pivots about the pivot axis of the dog 66, the lever being connected by a conductive rod (62) to an eccentric articulation (61) of the rotating part can be driven.   -42 - 13 Weapon according to claim 12 and one of   claims 3 or 5, characterized by the fact   that the coupling of the cocking lever (65) and the mass of inertia (42) is designed so that a striker spring (67) is maximally banded at the latest at the moment when the pressure of the gas fall.   14 A weapon according to one of claims 2 to 13, characterized   characterized in that the axis of rotation of the mass of inertia and the axis of rotation of the dog (66) and the cocking lever (65) are parallel and spaced apart on a plane in which a piece (rod 60 ) coupled to the mass of inertia moves under the action of the piston and in that the angle formed by the cocking lever (65) and the conductive rod (62)   when the weapon is armed, is approximately   9 Q O and that the position of the crank is   about 300 after the top dead center.   Weapon in particular according to one of the claims   previous years, provided for the introduction of a   key in the chamber (9) being in the feed position of a feed mechanism (105) which is actuated by two orbiforms (44, 46) which are integrally connected to an operating wheel (48, 50, 51). ) which actuates the yoke (4), each orbiform being constantly in contact with two parallel opposite edges (90, 91, 97, 98) of a lever, these two pairs of edges forming an angle of O 'with respect to to the other, characterized in that the first orbiform (44) is coupled to a first operating lever (first control plate 88) which pivots about an axis integral with the barrel (threaded shaft 86) and thereby that the second orbiform (46) is coupled to a second operating lever (second control plate 95), one end of which is articulated on a bent lever (99) constituting the feed mechanism and of which the other end is articulated on the first operating lever at a determined distance from its pivot (articulation 93).