EP1024339A2 - Munitionsmagazin für gurtlose geführte Munition - Google Patents

Munitionsmagazin für gurtlose geführte Munition Download PDF

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Publication number
EP1024339A2
EP1024339A2 EP00101368A EP00101368A EP1024339A2 EP 1024339 A2 EP1024339 A2 EP 1024339A2 EP 00101368 A EP00101368 A EP 00101368A EP 00101368 A EP00101368 A EP 00101368A EP 1024339 A2 EP1024339 A2 EP 1024339A2
Authority
EP
European Patent Office
Prior art keywords
ammunition
chain
tensioning
movement
tension
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
EP00101368A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1024339A3 (de
EP1024339B1 (de
Inventor
Rudi Beckmann
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 EP1024339A2 publication Critical patent/EP1024339A2/de
Publication of EP1024339A3 publication Critical patent/EP1024339A3/de
Application granted granted Critical
Publication of EP1024339B1 publication Critical patent/EP1024339B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F41—WEAPONS
    • F41A—FUNCTIONAL FEATURES OR DETAILS COMMON TO BOTH SMALLARMS AND ORDNANCE, e.g. CANNONS; MOUNTINGS FOR SMALLARMS OR ORDNANCE
    • F41A9/00—Feeding or loading of ammunition; Magazines; Guiding means for the extracting of cartridges
    • F41A9/61—Magazines
    • F41A9/64—Magazines for unbelted ammunition
    • F41A9/76—Magazines having an endless-chain conveyor

Definitions

  • the invention relates to an ammunition magazine for beltless guided ammunition with at least one endlessly guided Ammunition guide chain for conveying the ammunition in the ammunition magazine and a chain tensioning means for tensioning the Ammunition guide chain with a given chain tension, which is one for increasing chain tension Clamping movement in the clamping direction and to lower the Chain tension a tension movement against the tension direction carries out.
  • Such an ammunition magazine is from generic EP-078 482 B1 known.
  • a disadvantage of this clamping system is that the spring force accelerating the ammunition chain can be overcome, the spring thus engages and consequently the ammunition guide chain becomes loose. This is mainly because the spring constant accordingly must be dimensioned low. Does that change from the spring exerted clamping force in the case of thermal conditions Material stretches if the spring is accordingly the expansion movements of the ammunition guide chain on or disengages, the resulting tension force of the spring not be too strong or too weak for the material the ammunition chain is not too stressed becomes.
  • DE-36 44 513 C2 is also an ammunition magazine with a beltless, endless ammunition guide chain known.
  • Two opposing short ones Loops of the ammunition chain, one of which is coupled to an ammunition transfer device, are slidably guided in the conveying direction.
  • the shifting movement is powered by a prestressed gas pressure spring supported.
  • the drive unit of the ammunition guide chain is in this short loop with coupled ammunition transfer device, so that at Accelerate or slow down the ammunition chain initially just the inert mass of the short loop must be moved.
  • the movement of the remaining ammunition chain is namely through the slidably guided Loops uncoupled for now. So you can short acceleration times with comparatively weak dimensioned drive unit.
  • This publication does not go into clamping devices with which the chain tension of the ammunition guide chain is set can be.
  • a disadvantage of the known ammunition magazines with chain tensioners is that the chain tensioner in particular when accelerating or braking the ammunition guide chain Engages or disengages, in which there is mainly an undesirable lot in the ammunition guide chain can come.
  • the invention is based, an ammunition magazine the task of the type mentioned at the beginning, in which especially when accelerating the ammunition chain no lots can arise.
  • the invention solves this problem with an ammunition magazine of the type mentioned above with the characteristic Features of claim 1.
  • the chain tensioning means then has a means for influencing the spring constant of the chain tensioning device of the tension direction and the speed of the Clamping movement.
  • This measure can be advantageous various movement situations of the ammunition guide chain (thermally induced material expansion, acceleration or braking, etc.), which in turn influence have on the tensioning movement of the chain tensioning device, Be taken into account in such a way that in particular a Loose in the ammunition guide chain avoided if possible becomes.
  • This means of influencing the spring constant can for example functionally parallel to the chain tensioning device be switched so that it moves the chain tensioner can influence accordingly.
  • It can is an electromechanical component, such as a Eddy current brake act depending on the direction and the speed of the clamping movement their braking force changes.
  • a suitable measuring device can be provided for this be the movements of the eddy current brake detected and controls their braking resistor accordingly.
  • the agent may also be a hydraulic one Act element whose hydraulic working pressure is controlled depending on the speed and direction (if necessary also by a measuring device which the movements of the hydraulic element detected).
  • There are also numerous other configurations of this like means of conceivable, like cylinder-piston arrangements with one suitable hydraulic fluid, whose viscosity (e.g. through electric fields) can be adjusted accordingly, etc.
  • ammunition chain is only in the to understand figuratively, because the ammunition for example also by straps or bands through the ammunition magazine run in an endless loop can.
  • the term is only for easier readability of the present description, however, is not restrictive to understand.
  • the ammunition magazine can also be used for conveying and storing other items are used.
  • the term "spring constant" only denotes the proportionality factor (preferably first order) between the deflection of the chain tensioning device and the resulting restoring force. This term is meant to does not imply that only spring tension means as Chain tensioners are to be provided, but in turn serves only to make the present description easier to read.
  • a controlled hydraulic cylinder as a chain tensioner, for example fixed default (possibly saved in a table beforehand) Relationship between engagement and disengagement a hydraulic cylinder of this hydraulic chain tensioner and the one subsequently applied to the cylinder Pressure.
  • a spring there is a predetermined relationship between the Engagement and disengagement movement and the restoring force, too if this depends on the position, for example, and can be set differently for each position. The from a pair of values of the position of the engagement or disengagement movement and the restoring force acting there The proportionality factor should define the spring constant.
  • the agent preferably influences the spring constant in such a way that this with a tensioning movement of the chain tensioning means essentially independent of speed in the clamping direction and is a value to set assumes the specified chain tension (claim 2). It is therefore advantageous when the ammunition guide chain moves, which, for example, a lot in the same caused the spring constant not to change, so that the chain tension with such a tensioning movement of the chain tensioning means essentially their predetermined Can take on value. In this respect, it is this special situation around the normal case of a known Chain tensioning device, its spring constant in all situations remains unchanged.
  • the agent preferably influences the spring constant in such a way that this with a tensioning movement of the chain tensioning means against the tensioning direction at low speed the tensioning movement, in particular due to heat-related material expansion, essentially the Assumes the value for setting the specified chain tension, and at high speed of the clamping movement, especially when the ammunition chain is conveyed, takes on such a high value that the Tension movement against the tension direction essentially is blocked (claim 3). Towards a tensioning movement the direction of tension thus becomes two cases from each other distinguished, namely that of a slow and that of a quick tensioning movement.
  • the spring constant of the chain tensioning device is chosen in this way be that in the range due to thermal expansion occurring changes in length of the ammunition guide chain the chain tension does not vary too much.
  • the chain tensioning means is a spring means (claim 4). If other criteria are met, the chain tensioner can also a gas pressure spring or the like his.
  • the means for influencing the spring constants is preferred one functionally parallel with the chain tensioner coupled hydraulic cylinder with check valve, the check valve is designed so that it opens when there is a clamping movement in the clamping direction (claim 5).
  • This in turn is advantageous simple design of the means for influencing the Spring constants created.
  • the hydraulic cylinder can be dimensioned in such a way that it can be engaged or disengaged its piston required force with slow on or. Disengagement is essentially zero, while it essentially with a rapid movement of the pistons Is infinite. This can e.g. B. through the gap between Pistons and cylinders can be adjusted.
  • the check valve takes into account the case that the hydraulic Cylinder during a tensioning movement of the chain tensioning device against the clamping direction regardless of the speed the tensioning movement no braking forces should cause, whereby the resilience only of the fixed spring constants of the chain tensioning device.
  • the chain tensioning means preferably engages one for tensioning of the ammunition guide chain Seesaw on, each of the two ends of the seesaw with a Deflection unit for forming a loop with the ammunition guide chain is coupled and to the ammunition guide chain a transfer device for transfer and / or taking over ammunition or ammunition remnants is provided, which - seen in the chain course - between the two deflection units is arranged (claim 6).
  • this rocker device known as such by accelerating the ammunition chain tensile forces occurring in the chain absorbed by the rocker.
  • the means to influence is blocked the spring constant the engagement movement of the Chain tensioner so that in corresponding with the drive coupled sections of the ammunition guide chain very high tensile forces can occur.
  • the transfer device for example, transfers the cartridge to another ammunition feeder which the Ammunition in turn to a rapid-fire weapon transported.
  • the transfer device can synchronize with the transfer receive empty ammunition cases or similar and feed into the ammunition chain.
  • Two drive units are preferred for driving the Ammunition guide chain provided, each - in the chain course seen - in front of and behind the transfer device are provided, namely - seen in the course of the chain - in front of the first and behind the second deflection unit (Claim 7). These two drive units are advantageous so arranged that they guide the ammunition chain detached from the one between the seesaw Drive section of the ammunition chain can.
  • the ammunition magazine particularly preferably has one Measuring device for measuring the rocker position and one with the measuring device and the two drive units coupled Control device for controlling the two Drive units depending on the rocker position (Claim 8).
  • Both drive units can be advantageous now be controlled so that they try the rocker always bring to their zero position.
  • the drive units can accelerate accordingly slower, so that the acceleration forces acting on the ammunition guide chain are lower. In this respect lies for in this case the above-mentioned driving of the two sections of the ammunition chain. Fast acceleration of the transfer device drive are thus in a seesaw movement of the seesaw recorded the correspondingly slower of the two Drive units is compensated again.
  • the transfer device with another is preferred endless ammunition supply chain for feeding Ammunition coupled into a firearm, the ammunition supply chain guided over at least two deflection units one of the deflection units for feeding the ammunition intermittently driven into the firearm and the at least one non-driven deflection unit is provided with a locking device which a movement of the deflection unit against the ammunition feed direction blocks (claim 9).
  • the ammunition feed movement usually intermittent, i.e. H. there are short rapid accelerations and a subsequent standstill on.
  • the firearm usually serves as a drive for both the ammunition supply chain and the transfer device and the ammunition guide chain in the ammunition magazine. So the total inert mass of this Units accelerated with every shot and then be braked again.
  • the ammunition supply chain of the Ammunition feeder is, however, in some ways elastic and caused by appropriate restoring forces a reciprocating rotary movement of the transfer device, or the non-driven deflection unit as well as the ammunition guide chain in the ammunition magazine.
  • the latter units have one large inertial mass so that the acceleration forces with the corresponding back and forth movement accordingly are great.
  • the non-driven deflection unit moves in the opposite direction the direction of ammunition feed, the drive of the driven Deflection unit at the next acceleration (the next shot) apply a great force to this movement taking place in the opposite direction first slow down and then in the right direction to accelerate.
  • the drive of the pulley should be so be disproportionately trained so that he can bring up this acceleration.
  • the locking device has an advantageous effect on the non-driven deflection unit such that such opposite rotation can not occur.
  • the driven deflection unit must therefore the entire system just accelerate in the feed direction, not how first brake as described above. Can thus be advantageous the drive of the driven deflection unit is dimensioned weaker his. They are also on the ammunition supply chain acting loads lower.
  • FIG. 1 an ammunition magazine 2 is shown, in which a endless ammunition guide chain 6 cartridges 4 in Direction of funding A promotes.
  • the ammunition guide chain 6 consists of two highly tear-resistant parallel transport chains, their distance from each other is essentially the Cartridge length corresponds. They are at a constant distance two parallel transport chains over crossbars 8 with each other connected. The distance between the cross bars 8 from each other is essentially equal to the cartridge diameter plus the diameter of a cross bar 8 and one certain scope for the freedom of movement of the guided Cartridges 4.
  • the endless ammunition guide chain thus formed 6 is in several loops over pulleys 10, 12, 14 and 16 by the one shown in FIG Section of the ammunition magazine 2 out.
  • the cartridges 4 are inside the ammunition magazine 2 guided in guideways 18 with little clearance, which, for example, with sliding / roller tracks made of low-wear Plastics are provided.
  • the rigid, thin Cross bars 8 separate two successive ones Cartridges or their sleeves from each other and promote them through the guideway 18 in the ammunition magazine 2.
  • the crossbars 8 can be adapted to the cartridge shape Have profile with which tilting of the cartridges 4th is avoided if possible. Furthermore, the cross bars 8 axially rotatable on the two chains of the ammunition guide chain 6 attached to the unrolling of the cartridges 4 within the guideway 18 and thus also on to facilitate the crossbars 8.
  • the cartridges are over a feed wheel 20 and transfer wheels 22 and 24 to an ammunition feeder 25 handed over.
  • the ammunition feeder 25 has an ammunition supply chain 26 on that in an endless loop around a first 28 and a second 30 pulley is guided and several successive bowl-shaped receptacle 32 forms.
  • the receptacles 32 are dimensioned so that they can each hold a cartridge 4.
  • the ammunition supply chain 26 is in turn within a guideway 34 performed.
  • a self-retracting firearm may be provided, which the cartridges fed from the ammunition supply chain 26 takes over, shoots and the empty cartridge cases in turn passes to the ammunition supply chain 26.
  • cartridges 4 are thus removed from the ammunition guide chain 6 in the conveying direction A to the feed wheel 20 transported, from there forcibly over the Transfer wheel 22 to a corresponding receptacle 32 passed to the ammunition supply chain 26 while simultaneously one - seen in feed direction B - further forward lying cartridge on the second guide roller 30 of one Firearm, not shown, is loaded.
  • the empty cartridge cases are also on the pulleys 16 and 12 transported further.
  • the feed wheel 20 and the two transfer wheels 22 and 24 are positively connected to the first deflection roller 28, so that the attacking over the second pulley 30 Firearm retraction the ammunition supply chain 26, the first pulley 28, the two Transfer wheels 22 and 24, the feed wheel 20 and also the Ammunition guide chain 6 drives.
  • the feed wheel 20 can have a large connection angle range the ammunition supply chain 26 to the ammunition magazine 2 be covered.
  • Each loop of the ammunition guide chain 6 forming first and second deflecting rollers 14 and 16 are in Direction of conveyance A of the ammunition guide chain 6 is displaceable arranged. For this, reference is made to FIG. 2.
  • Fig. 2 shows a schematic side view of the in Fig. 1 shown ammunition magazine 2.
  • the first Carriage 40 is over rollers 44 and 46 in the first Link rail 36 guided and carries the Axis of the first deflection roller 14.
  • the second is also Carriage 42 over rollers 48 and 50 in the second link rail 38 guided and carries the axis the second deflection roller 16.
  • On the first carriage 40 the end of a first linkage 52 is pivotally attached, the other end with the first end of a seesaw 54 is pivotally connected.
  • the end is one second linkage 56 pivotable on the second carriage 42 attached while the second end of the second linkage 56 can be pivoted with the second end of the rocker 54 connected is.
  • the rocker 54 in turn is over one Pivot axis 58 is displaceable in a further link rail 60 guided.
  • the ammunition guide chain 6 via the sliding rocker 54, the two linkages 52 and 56, the two slides 40 and 42 and the two deflection rollers 14 and 16 either tensioned or be relaxed.
  • the firearm can feed wheel 20 drive, intermittently in the launch stroke of the Cartridges.
  • the ammunition chain 6 accelerated strongly initially and then slowed down again.
  • Tensile forces due to their inertial mass due to the numerous existing cartridges is very high.
  • This traction during the rocker 54 compensates for the acceleration phase, by the first deflection roller 14 during acceleration in the embodiment shown in FIG is moved to the right, whereby only the one between the feed wheel 20 and the first deflection roller 14 Section of the ammunition guide chain 6 accelerated must become.
  • Between the feed wheel 20 and the second deflection roller 16 would also create lots in the ammunition chain 6 arise, which, however, by the seesaw 54 is compensated.
  • the first deflection roller is moving 14 to the right in FIG. 1, i. H. the mobile Carriage 40 to the left in FIG. 2, so the Carriage 42 of rocker 54 is forcibly shown in FIG. 2 moved to the right, which in turn is a movement of the second Deflection roller 16 means in Fig. 1 to the left.
  • a rocker 54 mounted in a fixed position would thus be the the shortening of the loop shown in Fig. 1 between Feed wheel 20 and first guide roller 14 resulting lots between feed wheel 20 and second deflection roller 16 exactly canceled.
  • a toothed segment 62 is rigidly connected to the rocker 54, in which a gear 64 engages.
  • the gear 64 is actuated
  • the potentiometer 68 is one as a bridge branch Wheatstone bridge, not shown, switched, whose other bridge branch consists of two series connected There is resistance.
  • This output signal one is positively connected to the deflection roller 10 Drive (not shown) supplied. The drive is controlled so that he try to rocker 54th to pivot back to the rest or zero position.
  • Deflection roller 10 is the firearm generated intermittent movement of the ammunition supply chain 26 and the feed wheel 20 in a possible smooth movement of the ammunition guide chain 6 converted.
  • 3 and 3a show a cross section through the ammunition magazine 2.
  • the cut is made through a central surface along the link rail 60 of the rocker 54.
  • the rocker 54 is on provided on both side surfaces of the ammunition magazine 2.
  • the respective pivot axis 58 of the rocker 54 is in one Cross bridge 70 mounted, which the two rockers 54 with each other connects.
  • the cross bridge 70 is inside the link rails 60 slidable on both sides guided.
  • a chain tension spring 72 provided on both sides acts between the rigid housing of the ammunition magazine 2 and the displaceably guided cross bridge 70. This is the Chain tension spring 72 in a rigid with the housing of the Ammunition magazine 2 connected spring guide cylinder 74 held while their free moving end over one Spring guide rod 76 presses against the cross bridge 70. All in all the chain tension spring 72 presses the entire rocker 54 in the embodiment shown in FIG. 2 to the right, whereby the two shown in Fig. 1 Deflection rollers 14 and 16 also pushed to the right become. As a result, the ammunition guide chain 6 with pre-tensioned a certain predetermined chain tension. The chain tension results from the spring constant the chain tension spring 72 and its engagement position. The linear applies to ordinary spiral springs Hook's law on wide areas of the engagement position.
  • the spring constant of the chain tension spring 72 to increase so much that such a case essentially can be excluded does not lead to the goal here. With large spring constants, this is from the chain tension spring 72 clamping force already exerted after engagement the same over a short distance so strong that the ammunition guide chain 6 is unnecessarily tense, whereby Management problems and material fatigue occur can. Such a short distance indentation of the chain tension spring But 72 can already, for example thermally induced material strains are caused, because different materials for the housing of the ammunition magazine 2 (aluminum, carbon fiber composites, etc.) and the ammunition guide chain 6 (steel, etc.) be used. In this respect, the spring constant of the Chain tension spring 72 can be chosen so that even at strong temperature changes and the associated Engaging and disengaging movements from the chain tension spring 72 tension force exerted on the ammunition guide chain 6 stays in reasonable areas.
  • a hydraulic cylinder 78 is provided, the cylinder of which is rigid with the spring guide cylinder 74 connected is.
  • a Piston 80 parallel to the direction of action of the chain tension spring 72 out.
  • a piston rod 82 of the piston 80 is via a T-groove 84 with the cross bridge 70 non-positively connected.
  • a ball check valve 86 provided that when the Piston 80 closes in the cylinder, the closing movement is essentially caused by a spring means.
  • the ball check valve opens 86 due to the ventilation duct of the Ball check valve 86 flowing hydraulic fluid in the hydraulic cylinder 78.
  • the hydraulic cylinder 78 is dimensioned so that that he quickly engages his piston 80 opposes an essentially infinite resistance. Blocked with such a rapid engagement movement the hydraulic cylinder 78 thus via the piston rod 82 the movement of the cross bridge 70 in the in FIG. 3 illustrated embodiment to the left. A rapid movement of the cross bridge 70 to the left occurs as executed above in the event that the feed wheel 20 the Ammunition chain 6 accelerates.
  • the hydraulic Cylinder 78 therefore increases the spring constants in total the chain tension spring 72 to a value of almost infinite. This corresponds to the case that the cross bridge 70 or the rocker 54 rigid with the housing of the ammunition magazine 2 is connected.
  • a chain adjustment means 90 is also shown, that on the feed wheel 20 or the first deflecting roller 28 works.
  • the chain adjustment means 90 has a pivotable Worm gear 92 on that by a drive shaft stub 94 can be operated from.
  • On the axis of the Feed wheel 20 or the first deflection roller is rigid Gear ring 96 attached to the outside of the housing into which the swiveled Worm gear 92 can intervene. Consequently can the position of the ammunition guide chain 6 by means of Turning the worm gear 92, which in the pivoted Condition the ring gear 96 and thus the feed wheel 20 or the first deflection roller 28 rotates.
  • Fig. 4 shows a plan view of a freewheel with detachable Lock for the first pulley 28.
  • the first deflection roller is decelerated accordingly 28 from the second deflection roller 30 via the ammunition supply chain 26 driven.
  • the second pulley is located between the shots 30 silent while the ammunition supply chain 26 due to their inert mass and the restoring forces cannot immediately go to sleep.
  • the upset or stretched chain sections cause restoring forces in the ammunition supply chain 26 which the first deflection roller 28 to a reciprocating Bring rotation.
  • the Ammunition supply chain 26 on the cartridge supply side in the feed direction B accelerates, so it can be the worst Case that the guide roller 28 just one Performs rotational movement in the opposite direction.
  • the guide roller 28 moves a large inert mass.
  • This inert mass must now be driven by the Deflection roller 30 are overcome so that the first Deflection roller 28 first braked and then in a Rotary movement brought in the direction of feed B. becomes.
  • the drive of the guide roller 30 in accelerate a very large mass in this case this drive must be disproportionately large and the ammunition supply chain 26 would be disproportionate should be highly resilient.
  • the first deflection roller 28 is rigidly coupled to a freewheel 119 (see also Figure 2), the rotational movement of the first deflection roller 28 against the feed direction B locks. Thanks to this freewheel 119, no acceleration the deflection roller 28 and the units coupled therewith occur more against the feed direction B, so that the drive of the second deflection roller 30 always only the total inertial mass of the ammunition supply chain 26 accelerate, but does not have to slow down first.
  • the drive always turns the second deflection roller 30 into one brings predetermined location, which, for example, by the Firing mechanism of a self-retracting firearm is now determined by the extension of the ammunition supply chain 26 on the cartridge feed path and the associated restoring force the first deflection roller 28 then rotated so far in the feed direction B that the ammunition supply chain 26 on the cartridge supply side is slightly compressed.
  • This has a subsequent acceleration the second deflection roller 30 in total less force to apply because of this acceleration positively biased ammunition supply chain 26 one Put part of your chain tension in the acceleration can.
  • the chain part on the cartridge case discharge track is stretched to the same extent as the one Part is compressed on the cartridge feed side. In order to but face such on both lanes through the Ammunition supply chain 26 caused resetting forces, that the acceleration by the second pulley 30th is supported.
  • the freewheel 119 is not explained in more detail below. because its function and structure from the state of the art is well known. Otherwise, for the Freewheel 119 any other suitable type of locking means are used, the rotation of the first pulley 28 allowed in one direction and in the other Direction essentially (preferably rigid) blocks.
  • the freewheel 119 If the freewheel 119 is used as the blocking means, then its locking effect in one direction of rotation in principle not easily solvable. To the free wheel 119 to allow this blocking effect to be released anyway the freewheel 119 with an additional releasable lock coupled, which is explained in more detail below with reference to FIG. 4 becomes.
  • Fig. 4 shows such a releasable lock with the Freewheel 119 is non-positively coupled.
  • the freewheel sits in a ratchet wheel 102 and is rigid coupled to the first deflection roller 28.
  • a housing 115 this releasable lock has one in engagement with the Pawls of the ratchet wheel 102 standing locking cylinder 108 on.
  • the locking cylinder 108 has a flat end face on, when disengaged by an eccentric shaft 112 Lock cylinder 108 on the steep flanks of the pawls Pawl wheel 102 strikes. This will turn the Pawl wheel 102 in the embodiment shown in FIG. 4 locked clockwise.
  • the locking cylinder 108 is guided in the housing 115 which the locking cylinder 108 is substantially tangential can be disengaged in the direction of the ratchet wheel 102.
  • the release movement is caused by the eccentric shaft 112 which can be actuated via a rotary rod, not shown is.
  • This locking pin 116 is by the spring force a spring 118 pressed into this recess.
  • the Eccentric shaft 112 is aligned with the recess in such a way that the locking pin 116 when fully disengaged Lock cylinder 108 engages in the recess. This prevents the eccentric shaft 112 from being disengaged Lock cylinder 108 and thus locked ratchet 102 is rotated unintentionally.
  • the end face of the Locking pin 116 is designed such that with an appropriate torque on the Eccentric shaft 112 the recess from the locking pin 116 is released so that the eccentric shaft 112 is rotated and thus the locking cylinder 108 into the housing 115 is indentable.
  • the pawls of the ratchet wheel 102 can then when the ratchet wheel 102 moves clockwise insert the locking cylinder 108 into the housing 115, so that the locking effect on the ratchet wheel 102 in this Direction of rotation is canceled.
  • the locking cylinder 108th and a corresponding pawl of the ratchet wheel 102 to each other are positioned so that the eccentric shaft 112 not in the fully disengaged position of the cylinder 108 can be rotated.
  • one of these Resistance disengaging the locking cylinder 108 the ratchet wheel 102 unintentionally in one direction are rotated, in which the freewheel 119 locks.
  • the first deflection roller 28 becomes again moved and thus the previously adjusted in their position Ammunition feed chain 26 misaligned again.
  • the distance between the two Cylinder 108 and 114 is dimensioned such that with cylinder 114 fully disengaged when the hemispherical end face exactly between two Pawls, an optimal position of the locking cylinder 108 with respect to the pawls, so that the eccentric shaft 112 fully disengage the locking cylinder 108 can.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Controlling Rewinding, Feeding, Winding, Or Abnormalities Of Webs (AREA)
  • Tension Adjustment In Filamentary Materials (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of El Displays (AREA)
  • Telephone Function (AREA)
  • Control Of Indicators Other Than Cathode Ray Tubes (AREA)
EP00101368A 1999-01-28 2000-01-24 Munitionsmagazin für gurtlose geführte Munition Expired - Lifetime EP1024339B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19903347 1999-01-28
DE19903347A DE19903347C1 (de) 1999-01-28 1999-01-28 Munitionsmagazin für gurtlos geführte Munition

Publications (3)

Publication Number Publication Date
EP1024339A2 true EP1024339A2 (de) 2000-08-02
EP1024339A3 EP1024339A3 (de) 2001-07-25
EP1024339B1 EP1024339B1 (de) 2004-05-12

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Family Applications (1)

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EP00101368A Expired - Lifetime EP1024339B1 (de) 1999-01-28 2000-01-24 Munitionsmagazin für gurtlose geführte Munition

Country Status (6)

Country Link
EP (1) EP1024339B1 (no)
AT (1) ATE266850T1 (no)
AU (1) AU752264B2 (no)
DE (2) DE19903347C1 (no)
ES (1) ES2218004T3 (no)
PT (1) PT1024339E (no)

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WO2004097256A1 (de) * 2003-04-25 2004-11-11 Heckler & Koch Gmbh Kettenabstreifer

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DE102005003751B3 (de) * 2005-01-27 2006-07-20 Rheinmetall Waffe Munition Gmbh Hülsenauffangeinrichtung für eine gurtgliedlose Munition
DE102006006961A1 (de) 2006-02-14 2007-08-23 Oerlikon Contraves Ag Munitionszuführung mit automatischer Kupplung

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US4573395A (en) 1983-12-19 1986-03-04 Ares, Inc. Linkless ammunition magazine with shell buffer
EP0078482B1 (en) 1981-10-26 1987-03-25 Western Design Corporation Transport mechanism
DE3644513C1 (de) 1986-12-24 1992-08-27 Dornier Gmbh Munitionszufuehrung

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EP0152549A1 (de) * 1983-12-22 1985-08-28 Werkzeugmaschinenfabrik Oerlikon-Bührle AG Vorrichtung zum Zuführen von Patronen zu einer Feuerwaffe
EP0361050B1 (de) * 1988-09-28 1992-02-26 Oerlikon-Contraves AG Endlose Speicher- und Förderkette in einem Munitionsmagazin
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EP0078482B1 (en) 1981-10-26 1987-03-25 Western Design Corporation Transport mechanism
US4573395A (en) 1983-12-19 1986-03-04 Ares, Inc. Linkless ammunition magazine with shell buffer
DE3644513C1 (de) 1986-12-24 1992-08-27 Dornier Gmbh Munitionszufuehrung

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004097256A1 (de) * 2003-04-25 2004-11-11 Heckler & Koch Gmbh Kettenabstreifer

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AU752264B2 (en) 2002-09-12
ES2218004T3 (es) 2004-11-16
AU1358900A (en) 2000-08-03
PT1024339E (pt) 2004-09-30
ATE266850T1 (de) 2004-05-15
DE50006362D1 (de) 2004-06-17
EP1024339A3 (de) 2001-07-25
DE19903347C1 (de) 2000-08-17
EP1024339B1 (de) 2004-05-12

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