EP0185871B1 - Lifting gun mount for battle tanks - Google Patents

Lifting gun mount for battle tanks Download PDF

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Publication number
EP0185871B1
EP0185871B1 EP85113164A EP85113164A EP0185871B1 EP 0185871 B1 EP0185871 B1 EP 0185871B1 EP 85113164 A EP85113164 A EP 85113164A EP 85113164 A EP85113164 A EP 85113164A EP 0185871 B1 EP0185871 B1 EP 0185871B1
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EP
European Patent Office
Prior art keywords
barrel
return
braking
gun
piston
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Expired
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EP85113164A
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German (de)
French (fr)
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EP0185871A1 (en
Inventor
Gert Winkler
Erich Zielinski
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Rheinmetall Industrie AG
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Rheinmetall GmbH
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Publication of EP0185871A1 publication Critical patent/EP0185871A1/en
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    • 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
    • F41A23/00—Gun mountings, e.g. on vehicles; Disposition of guns on vehicles
    • F41A23/20—Gun mountings, e.g. on vehicles; Disposition of guns on vehicles for disappearing guns
    • 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
    • F41A25/00—Gun mountings permitting recoil or return to battery, e.g. gun cradles; Barrel buffers or brakes

Definitions

  • the invention relates to a swiveling crest mount for the weapon barrel of a main battle tank according to the preamble of claim 1.
  • DE-C-317 025 discloses braking cylinders arranged on both sides of the weapon barrel on the height-adjustable cradle for braking the return movement of the weapon barrel and two brake cylinders arranged in their parallel position, which cannot be changed for the gun embedding, on the lower carriage receiving the cradle.
  • brake cylinders are therefore not suitable as brake means for the installation of a piston-cylinder unit known from US-A-4,326,446 and required for adjusting the fire height, because maintaining an approximately constant braking force is not guaranteed.
  • DE-C-317 025 such an application is not provided on the one hand and is also not possible on the other hand, because the weapon barrel can only be swiveled around the shield pin axis only for the leveling process and a manually driven lever mechanism is used for this, which cannot be adjusted to the height of the fire by changing the height of the shield pin axis.
  • the brake cylinders known from DE-C-317 025 due to their structure and mode of operation, are not able to be used as lifting cylinders for swinging up a gun arm carrying the barrel weapon, so that a separate lifting cylinder unit would also be necessary for swinging up.
  • a compensation cylinder which however does not function as a lifting and braking cylinder and therefore does not perform any braking work, but only serves to compensate for the pitching movement by a pair of forces occurring on the vehicle, the pair of forces being separated by a distance the shield pin axis to the tube core axis is generated.
  • the object of the invention is to design the crest mount for the weapon barrel of a main battle tank in such a way that weight and production costs are saved, the weapon barrel which is usually used in a tower of the main battle tank and which transmits a high shot energy with the associated, preferably known, preferably combined barrel return brake and generates a short return path Retrofit device can be used in a crest mount of a battle tank with a fire height greater than 4 m and, without jeopardizing the stability of the battle tank when firing a shot, a reduced and constant braking force can be achieved on the shield peg.
  • the invention makes it possible, in an advantageous manner, to make the pivoting movement of a gun arm carrying the weapon barrel usable for relieving the return energy of the gun barrel.
  • This saves weight and manufacturing effort, known gun barrels that can be used in armored turrets and that transmit high shot energy, as well as short-cycle, preferably combined return brake and tube recovery devices that contain a freewheel for the return, although the fire resistance of the armored vehicle is greater than 4 m non-endangering long return path for braking the weapon barrel is guaranteed.
  • the total return energy of the weapon barrel which also includes the return energy of the parts returning with the barrel, for example the rock-resistant return braking device, after the free-running of the return device has ended, at the same time during the pivoting back of the gun arm by the angle a Braking means of a piston-cylinder unit which adjusts the fire height of the weapon barrel and is absorbed in an energy-consuming manner by the tube return brake device having a short braking distance b in a known manner.
  • the braking areas a of the brake means and b of the return brake device can be adjusted to one another in such a way that the return path b remains comparatively short.
  • This results in braking areas a greater than b, preferably a / b 2/1, reducing the manufacturing effort and the weight, a comparatively short pipe return length within the cradle storage and comparatively small structural units for the return braking device, even with a large fire height there is the possibility of reducing the braking area b in such a way that the braking area a corresponds approximately to the maximum pipe return path c.
  • the braking means can be designed as a pressure-maintaining valve or as an electrohydraulic servo valve, the throttle cross section of the servo valve being controllable depending on the piston rod of the piston-cylinder unit moving back during the pipe return and pressure-dependent on the brake pressure generated in the return brake device, the braking force can also be advantageously controlled Keep approximately constant over the entire pipe return path, whereby the reduced braking force has a gentle effect on the mounting, the return brake device and the piston-cylinder unit.
  • the pivotable crest mount shown in Figures 1 and 2 for the weapon barrel 3 of a main battle tank 15 consists essentially of two gun arms 3 supporting the gun barrel 3 on both sides and two piston cylinder units 1 adjusting the height of fire h of the gun barrel 3.
  • the symmetrical arrangement of the gun arms 5 and Piston cylinder units 1 on both sides of the weapon barrel 3 are only visible in the side views of the crest mount, only one mount arm 5 and one piston cylinder unit 1.
  • the cylinders 8 of both piston-cylinder units 1 are connected to a part 16 of the armored vehicle 22 which can be oriented laterally about the axis 21 at the bearing points 17 and the piston rod 10 of each piston-cylinder unit 1 is pivotably connected to a bearing point 18 of a carriage arm 5 via bearing bolts 17 ', 18'.
  • the side-directional part 16 contains at the end 20 located opposite the bearing points 17 further bearing points 19, to which the carriage arms 5 are connected so that they can be pivoted up via bearing bolts 19 '.
  • the weapon barrel 3 is mounted within the weapon barrel cradle 14, whereby it can move back and forth within the weapon barrel cradle storage when the weapon barrel passes through a projectile 23 by a resistance-free barrel run d and a braking area b of a barrel return braking device 6, which is preferably also equipped with a recovery device (not shown).
  • the return and forward travel (b + d) of the return braking device 6 is short and corresponds comparatively to the short return travel of known return braking devices, which are used without braking the stability of known armored vehicles, for braking a weapon barrel used in the turret of a main battle tank and for transferring high shot energy.
  • known return brake and pipe recovery devices with free wheel and short brake stroke are known from DE-PS 3 015 097.
  • the cylinder 24 of the return brake device 6 is firmly connected in a known manner to the weapon barrel cradle 14, while its piston 25 is connected to the return and forward end 26 of the weapon barrel 3.
  • the gun barrel cradle 14 contains shield pins 13 arranged on both sides for storage in the carriage arms 5, around the axis of which the gun barrel 3 can be adjusted in height in an angular range ⁇ in an angle range ⁇ in a position 2 pivoted up by the piston cylinder units 1 at the fire height h by means of height adjustment cylinders 27 attached to each carriage arm 5.
  • the leveling cylinder 27 is able to stabilize the weapon barrel 3 in such a way that it maintains its targeted position when the firing position 28 is in the angular range ⁇ during the return and advance.
  • the main battle tank also contains a sighting device, not shown.
  • a pivoting loading device 29 is fastened to the weapon barrel cradle 14, the structure and function of which, however, is not essential to the invention and is therefore not explained further.
  • the piston-cylinder unit 1 is able to pivot the carriage arm 5 from an approximately horizontal starting position lying on the armored vehicle 22 into an almost vertical maximum position.
  • the storage of the gun barrel 3 be can be found in the starting position of the carriage arm 5 in a starting position 30 corresponding to the lowest fire height h '.
  • the piston-cylinder unit 1 With a comparatively flat and only a slight inclination angle of y less than 30 °, the piston-cylinder unit 1 is only a small space-saving piston stroke e for pivoting the carriage arm 5 the piston rod 10 required.
  • the position 18 moves in a circular path 31 around the bearing 19 such that the inclined position of the piston-cylinder unit 1 is changed only insignificantly.
  • Each piston-cylinder unit 1 is assigned a braking means 4 shown in FIGS. 4 to 6 and a control unit 33.
  • the braking means 4 serves the purpose of making the rearward pivoting movement of the carriage arm 5 in an angular range a in a return region a of the shield pins 13 and thus also of the weapon barrel 3 usable for the return energy relief of the weapon barrel 3 and the masses returning with the weapon barrel 3.
  • the braking means 4 is effective in every swiveled-up position 2 of the weapon barrel 3 when firing the shot, so that when the barrel returns after free running d of the barrel return braking device 6, the return energy of the barrel 3, of the breech 32 within a barrel return path c formed from the barrel return regions (a + b) and further masses returning with the weapon barrel 3, at the same time being absorbed in an energy-consuming manner by the piston-cylinder unit 1 via the carriage arm 5 pivoted back by the angle a corresponding to the barrel return area a and on the other hand by the tube-fixed barrel return brake device 6 which has returned to the area b.
  • the braking force F acting on the shield pin 13 is reduced in such a way that sufficient armor vehicle 22 stability at shot heights h greater than 4 m when used is typically used in the turret of a main battle tank and high shot energy transferable weapon barrels 3 exists. In this way, 22 fire heights h up to 8 m can be achieved with stable armor vehicle stability.
  • the weapon barrel 3 is braked exclusively in a known manner by the return brake device 6 within the return region b, because the piston rod 10 has reached its end position 34 pushed into the cylinder 8 and pivoting of the carriage arm 5 is not possible is. Due to the small braking area b, the braking force F 1 acting on the shield pin 13 is comparatively large, but the stability of the armored vehicle 22 is not endangered due to the low fire height h '.
  • the braking work A 1 of the return braking device 6 corresponds to the product of the force F 1 x braking area b and thus the rectangular area enclosed by the points A, B, C, D.
  • the braking means 4 of the piston-cylinder unit 1 and the hydraulic damping of the return brake device 6 are coordinated with one another during the simultaneous braking processes of the two brake devices 4, 6 such that the braking force F 2 acting on the shield pin 13 of the gun barrel cradle 14 is approximately constant within the tube return path c.
  • the braking work performed by the braking means 4 corresponds to the product F 2 xa and thus the rectangular area enclosed by the points B, E, F, G
  • the braking work performed by the return braking device 6 corresponds to the product F 2 xb and thus the Rectangular area enclosed by points A, B, G, H.
  • the total braking work A z thus corresponds to the rectangular area enclosed by the points A, E, F, H.
  • the horizontal return area a of the shield pin 13 and thus of the weapon barrel 3 decreases progressively smaller in the lower pivoting range of the carriage arm 5. Therefore, with the same braking ability A z and decreasing braking areas a of the braking means 4, the braking force increases by an amount exceeding the braking force F 2 until it has reached the amount of the braking force F again at the height of fire h '.
  • the brake means 4 is connected to a cylinder space 7, 7 ′ of the cylinder 8 belonging to the piston-cylinder unit 1, which displaces hydraulic medium during the pipe return and can be arranged inside the cylinder 8 or on the output side of the cylinder space 7 outside the cylinder 8.
  • a piston 42 which is slidable within the cylinder 8 and which is fastened to the piston rod 10 produces a further cylinder space 43, 43' which is necessary for moving the piston rod 10 on both sides.
  • the braking means 4 according to FIGS. 4 and 5 is integrated within a control unit 33.
  • the braking means 4 is an electrohydraulic servo valve 11, the flow cross section 36 of which, in order to achieve an approximately constant braking force profile 12 (FIG. 3), is path-dependent from the piston rod 10 of the piston-cylinder unit 1 moving back during the pipe run, via a control element amplifier 37 and pressure-dependent from the of the return brake device 6 can be throttled brake pressure via a pressure transmitter 35 connected to the control element amplifier 37.
  • the cylinder space 7 is connected via a line 44 to the throttled flow cross section 36 and the cylinder space 43 via a line 45 to a hydraulic energy source (not shown), the flow cross section into the cylinder space 43 also being throttled.
  • the servo valve 11 in the switching position 38 is able to move the piston rod 10 forward in the direction 39. whereby the carriage arm 5 (Fig. 1) moves the shield pin 13 back to position 2 forward.
  • the switching position 40 a change in the position 2 (FIG. 1) is not possible, while in the switching position 41 the piston rod 10 can be moved back in the opposite direction 39 and thus small fire heights h can be set.
  • the brake means 4 is designed as a pressure-maintaining valve 9, which is connected to a non-throttling 4/4 way valve 46 within the control unit 33 during the pipe return region a.
  • a predeterminable constant braking force can also be generated during the braking process.
  • the switch positions 38, 40, 41 required to adjust the fire height h correspond to the switch positions already described according to FIG. 4.
  • Fig. 6 illustrates the arrangement of a brake means 4 designed as a pressure-maintaining valve 9 'within the piston 42. Because the valve cone 47 only opens after a predetermined pressure has been overcome within the cylinder space 78, a braking movement of the piston rod 10 within the piston is maintained while maintaining a constant braking force Cylinder 8 possible. During the braking process, the line 44 'of the piston chamber 7' is closed. To adjust the fire height h (FIG. 1), a 4/3 directional control valve 48 with the other switching positions 38, 41 described above within the control unit 33 is required for this arrangement.
  • circuit symbols drawn in FIGS. 4 to 6 correspond to the international standard ISO 1219.
  • the crown mount only with a piston-cylinder unit 1 and an associated brake means 4. Accordingly, only one carriage arm 5 is also required for the height adjustment of the weapon barrel 3, which, however, bifurcates in the region of the shield pins 13 for fastening the weapon barrel 3 on both sides.

Description

Die Erfindung betrifft eine hochschwenkbare Scheitellafette für das Waffenrohr eines Kampfpanzers nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a swiveling crest mount for the weapon barrel of a main battle tank according to the preamble of claim 1.

Derartige Scheitellafettierungen sind bekannt und werden beispielsweise in der US-A-4 326 446 beschrieben.Such crest mountings are known and are described, for example, in US Pat. No. 4,326,446.

Beim Einsatz dieser Scheitellafettierung ist es bei vergleichsweise grossen Feuerhöhen grösser 4 m zur Erzielung einer ausreichenden Standfestigkeit des Kampfpanzerfahrzeuges notwendig, den Abbremsweg des bei Schussabgabe rücklaufenden Rohres gegenüber einem im Panzerturm gelagerten eine hohe Schussenergie übertragenden Waffenrohr um ein mehrfaches zu erhöhen. Es ergeben sich somit bei der Scheitellafettierung lange Rohrrücklaufwege mit der Notwendigkeit, die von der Scheitellafettierung aufgenommene Lagerung des rücklaufenden Rohres und die Rohrrücklaufbremseinrichtung sowie die Rohrvorholeinrichtung ebenso lang auszuführen.When using this crest mount, with comparatively large fire heights greater than 4 m, in order to achieve sufficient stability of the main battle tank vehicle, it is necessary to increase the braking distance of the barrel returning when the shot is fired by a multiple compared to a weapon barrel carrying high shot energy stored in the turret. This results in long pipe return paths in the crest mount with the need to carry out the storage of the return pipe taken up by the crest mount and the pipe return braking device as well as the pipe recovery device as long.

Derartige lange Waffenrohrlagerungen und Rohrbrems- sowie Rohrvorholeinrichtungen weisen jedoch nachteilig ein hohes Gewicht auf und verursachen einen nicht unbedeutenden fertigungstechnischen Aufwand.Such long weapon barrel mountings and barrel brake and barrel recovery devices, however, have a high weight and cause a not insignificant manufacturing outlay.

Aus der DE-C-317 025 sind zur Bremsung der Rücklaufbewegung des Waffenrohres einmal beidseitig des Waffenrohres an der höhenrichtbaren Wiege angeordnete Bremszylinder und auf der die Wiege aufnehmenden Unterlafette zwei in ihrer zur Geschützbettung unveränderbaren parallelen Lage angeordnete Bremszylinder bekannt.DE-C-317 025 discloses braking cylinders arranged on both sides of the weapon barrel on the height-adjustable cradle for braking the return movement of the weapon barrel and two brake cylinders arranged in their parallel position, which cannot be changed for the gun embedding, on the lower carriage receiving the cradle.

Bei diesen Bremszylindern sind jedoch keine Mittel ersichtlich, die am Schildzapfen der Waffenrohrwiege wirkende Bremskraft während des Bremsvorganges annähernd konstant zu halten, zumal der Bremsvorgang durch die veränderbare Kraft einer Vorholfeder beeinflusst wird.With these brake cylinders, however, no means are apparent to keep the braking force acting on the shield pin of the gun barrel cradle approximately constant during the braking process, especially since the braking process is influenced by the variable force of a return spring.

Diese Bremszylinder sind deshalb auch als Bremsmittel für den Einbau einer aus der US-A-4 326 446 bekannten und zum Einstellen der Feuerhöhe benötigten Kolbenzylindereinheit nicht geeignet, weil das Einhalten einer annähernd konstanten Bremskraft nicht gewährleistet ist.These brake cylinders are therefore not suitable as brake means for the installation of a piston-cylinder unit known from US-A-4,326,446 and required for adjusting the fire height, because maintaining an approximately constant braking force is not guaranteed.

Nach der DE-C-317 025 ist des weiteren ein derartiger Einsatz einerseits nicht vorgesehen und andererseits auch nicht möglich, weil das Waffenrohr ausschliesslich nur für den Höhenrichtvorgang um die Schildzapfenachse schwenkbar ist und dafür ein manuell antreibbarer Hebelmachanisms eingesetzt wird, der keine Verstellmöglichkeit der Feuerhöhe durch Veränderung der Höhenlage der Schildzapfenachse zulässt. Des weiteren sind die aus der DE-C-317 025 bekannten Bremszylinder durch ihren Aufbau und ihre Wirkungsweise nicht in der Lage, als Hubzylinder zum Hochschwenken eines die Rohrwaffe tragenden Lafettenarmes eingesetzt zu werden, so dass zum Hochschwenken eine separate Hubzylindereinheit zusätzlich notwendig wäre.According to DE-C-317 025, such an application is not provided on the one hand and is also not possible on the other hand, because the weapon barrel can only be swiveled around the shield pin axis only for the leveling process and a manually driven lever mechanism is used for this, which cannot be adjusted to the height of the fire by changing the height of the shield pin axis. Furthermore, the brake cylinders known from DE-C-317 025, due to their structure and mode of operation, are not able to be used as lifting cylinders for swinging up a gun arm carrying the barrel weapon, so that a separate lifting cylinder unit would also be necessary for swinging up.

Aus der FR-A-1 160 125 ist ein Kompensationszylinder bekannt, der jedoch nicht als Hub- und Bremszylinder fungiert, und somit keine Bremsarbeit verrichtet, sondern ausschliesslich den Ausgleich der Nickbewegung durch ein am Fahrzeug auftretendes Kräftepaar dient, wobei das Kräftepaar durch einen Abstand der Schildzapfenachse zur Rohrseelenachse erzeugt wird.From FR-A-1 160 125 a compensation cylinder is known, which however does not function as a lifting and braking cylinder and therefore does not perform any braking work, but only serves to compensate for the pitching movement by a pair of forces occurring on the vehicle, the pair of forces being separated by a distance the shield pin axis to the tube core axis is generated.

Aufgabe der Erfindung ist es, die Scheitellafettierung für das Waffenrohr eines Kampfpanzers derartig auszubilden, dass Gewicht und Fertigungsaufwand sparend, das in einem Turm des Kampfpanzers üblicherweise eingesetzte eine hohe Schussenergie übertragende Waffenrohr mit der dazugehörigen an sich bekannten einen kurzen Rücklaufweg erzeugenden vorzugsweise kombinierten Rohrrücklaufbrems-und Vorholeinrichtung bei einer Scheitellafettierung eines Kampfpanzers mit einer Feuerhöhe grösser 4 m einsetzbar ist und, ohne die Standfestigkeit des Kampfpanzers bei der Schussabgabe zu gefährden, eine reduzierte und konstante Bremskraft am Schildzapfen erzielbar ist.The object of the invention is to design the crest mount for the weapon barrel of a main battle tank in such a way that weight and production costs are saved, the weapon barrel which is usually used in a tower of the main battle tank and which transmits a high shot energy with the associated, preferably known, preferably combined barrel return brake and generates a short return path Retrofit device can be used in a crest mount of a battle tank with a fire height greater than 4 m and, without jeopardizing the stability of the battle tank when firing a shot, a reduced and constant braking force can be achieved on the shield peg.

Gelöst wird diese Aufgabe durch die im Patentanspruch 1 angegebene Erfindung. Die Unteransprüche nennen vorteilhafte Ausgestaltungen und Weiterbildungen.This object is achieved by the invention specified in claim 1. The subclaims name advantageous refinements and developments.

Die Erfindung ermöglicht es, in vorteilhafter Weise die Schwenkbewegung eines das Waffenrohr tragenden Lafettenarmes für die Rücklaufenergieentlastung des Waffenrohres nutzbar zu machen. Dadurch sind, Gewicht und Fertigungsaufwand sparend, bekannte in Panzertürmen einsetzbare und eine hohe Schussenergie übertragende Waffenrohre sowie kurzhübige, vorzugsweise kombinierte Rücklaufbrems- und Rohrvorholeinrichtungen, die für den Rücklauf einen Freilauf enthalten, einsetzbar, wobei trotzdem bei Feuerhöhen grösser 4 m ein die Standfestigkeit des Panzerfahrzeuges nicht gefährdender langer Rücklaufweg zur Abbremsung des Waffenrohres gewährleistet ist.The invention makes it possible, in an advantageous manner, to make the pivoting movement of a gun arm carrying the weapon barrel usable for relieving the return energy of the gun barrel. This saves weight and manufacturing effort, known gun barrels that can be used in armored turrets and that transmit high shot energy, as well as short-cycle, preferably combined return brake and tube recovery devices that contain a freewheel for the return, although the fire resistance of the armored vehicle is greater than 4 m non-endangering long return path for braking the weapon barrel is guaranteed.

In besonders vorteilhafter Weise wird bei der Schussabgabe die gesamte Rücklaufenergie des Waffenrohres, die auch die Rücklaufenergie der mit dem Rohr zurücklaufenden Teile, beispielsweise der wiegenfesten Rücklaufbremseinrichtung mit umfasst, nach beendetem Freilauf der Rücklaufeinrichtung, gleichzeitig während des Zurückschwenkens des Lafettenarmes um den Winkel a durch ein Bremsmittel einer die Feuerhöhe des Waffenrohres einstellenden Kolbenzylindereinheit und durch die in bekannter Weise einen kurzen Bremsweg b aufweisende Rohrrücklaufbremseinrichtung energieverzehrend absorbiert.In a particularly advantageous manner, when the shot is fired, the total return energy of the weapon barrel, which also includes the return energy of the parts returning with the barrel, for example the rock-resistant return braking device, after the free-running of the return device has ended, at the same time during the pivoting back of the gun arm by the angle a Braking means of a piston-cylinder unit which adjusts the fire height of the weapon barrel and is absorbed in an energy-consuming manner by the tube return brake device having a short braking distance b in a known manner.

Aufgrund dieser neben der wiegenfesten Rücklaufbremseinrichtung zusätzlichen Abbremsmöglichkeit des Rohrrücklaufs durch das Bremsmittel der Kolbenzylindereinheit lassen sich in einfacher Weise durch die Rückschwenkmöglichkeit des Lafettenarmes grosse Bremswege c des Waffenrohres mit einer vergleichsweise geringen am Schildzapfen wirkenden Bremskraft erzielen.On account of this additional braking possibility of the pipe return by the brake means of the piston-cylinder unit in addition to the cradle-proof return braking device, large braking distances c of the weapon barrel with a comparatively small braking force acting on the shield pin can be achieved in a simple manner by the pivoting back possibility of the carriage arm.

In Abhängigkeit von der Höhe der Bremsenergie, einerseits der Rücklaufbremseinrichtung und andererseits des Bremsmittels der Kolbenzylindereinheit, lassen sich die Bremsbereiche a des Bremsmittels und b der Rücklaufbremseinrichtung derartig zueinander einstellen, dass der Rücklaufweg b vergleichsweise gering bleibt. Dadurch ergeben sich bei Bremsbereichen a grösser b, vorzugsweise a/b = 2/1, den Fertigungsaufwand und das Gewicht reduzierend, eine vergleichsweise geringe Rohrrücklauflänge innerhalb der Wiegenlagerung und vergleichsweise kleine Baueinheiten für die Rücklaufbremseinrichtung, wobei sogar bei grosser Feuerhöhe die Möglichkeit besteht, den Bremsbereich b derartig zu reduzieren, dass der Bremsbereich a annähernd dem maximalen Rohrrücklaufweg c entspricht.Depending on the amount of braking energy, on the one hand the return brake device and on the other hand the brake means of the piston-cylinder unit, the braking areas a of the brake means and b of the return brake device can be adjusted to one another in such a way that the return path b remains comparatively short. This results in braking areas a greater than b, preferably a / b = 2/1, reducing the manufacturing effort and the weight, a comparatively short pipe return length within the cradle storage and comparatively small structural units for the return braking device, even with a large fire height there is the possibility of reducing the braking area b in such a way that the braking area a corresponds approximately to the maximum pipe return path c.

In vorteilhafter Weise lässt sich bei vergleichsweise kleinen Bremsbereichslängen b bekannter Rücklaufbremseinrichtungen und bei Feuerhöhen > 4m sowie Bremsbereichslängen a/b = 2/1 eine ausreichende Standfestigkeit des Panzerfahrzeuges bei Schussabgabe erzielen. beispielsweise wird bei einem in einer Feuerhöhe von 5, m an dem Lafettenarm über den Schildzapfen befestigten Kampfpanzerwaffenrohr bei einem Bremsbereichsverhältnis a/b = 2/1 eine die Standfestigkeit des Panzerfahrzeuges garantierende Reduzierung der am Schildzapfen angreifenden Bremskraft von 600 kN auf 200 kN erzielt.With comparatively small braking area lengths b of known reverse braking devices and with fire heights> 4m and braking area lengths a / b = 2/1, it is advantageously possible to achieve sufficient stability of the armored vehicle when firing a shot. For example, with a battle tank weapon barrel attached to the gun arm above the shield pin at a fire height of 5 m at a braking area ratio a / b = 2/1, a reduction in the armoring force guaranteeing the stability of the armored vehicle from 600 kN to 200 kN is achieved.

Dadurch, dass das Bremsmittel als Druckhalteventil oder als ein elektrohydraulisches Servoventil ausgebildet sein kann, wobei der Drosselquerschnitt des Servoventils wegabhängig von der sich während des Rohrrücklaufs zurückbewegenden Kolbenstange der Kolbenzylindereinheit und druckabhängig von dem in der Rücklaufbremseinrichtung entstehenden Bremsdruck steuerbar ist, lässt sich weiter vorteilhaft die Bremskraft über den gesamten Rohrrücklaufweg annähernd konstant halten, wobei sich die reduzierte Bremskraft schonend auf die Lafettierung, die Rücklaufbremseinrichtung und die Kolbenzylindereinheit auswirkt.The fact that the braking means can be designed as a pressure-maintaining valve or as an electrohydraulic servo valve, the throttle cross section of the servo valve being controllable depending on the piston rod of the piston-cylinder unit moving back during the pipe return and pressure-dependent on the brake pressure generated in the return brake device, the braking force can also be advantageously controlled Keep approximately constant over the entire pipe return path, whereby the reduced braking force has a gentle effect on the mounting, the return brake device and the piston-cylinder unit.

Die Erfindung wird anhand der in den Zeichnungen dargestellten Ausführungsbeispiele des näheren erläutert.The invention is explained in more detail with reference to the exemplary embodiments shown in the drawings.

Es zeigen:

  • Fig. 1 in einer Seitenansicht ein auf einem Kampfpanzer scheitellafettiertes Waffenrohr, mit einer den Rücklaufweg gemeinsam bremsenden wiegenfesten Rücklaufbremseinrichtung und einer Bremsmittel enthaltenden die Feuerhöhe des Waffenrohres einstellenden Kolbenzylindereinheit der Scheitellafettierung;
  • Fig. 2 in einer ausschnittsweisen Vergrösserung die in Fig. 1 dargestellte Scheitellafettierung des Waffenrohres.
  • Fig. 3 in einem Bremskraftdiagramm die Bremsarbeit der Rücklaufbremseinrichtung und des Bremsmittels der Kolbenzylindereinheit sowie die am Schildzapfen wirkende reduzierte Bremskraft;
  • Fig. 4 in einer schematischen Darstellung die Kolbenzylindereinheit mit einem als Bremsmittel ausgebildeten elektrohydraulischen Servoventil;
  • Fig. 5 in einer schematischen Darstellung ein ausserhalb der Kolbenzylindereinheit angeordnetes als Bremsmittel ausgebildetes Druckhalteventil;
  • Fig. 6 in einer schematischen Darstellung ein innerhalb der Kolbenzylindereinheit angeordnetes als Bremsmittel ausgebildetes Druckhalteventil.
Show it:
  • 1 is a side view of a gun barrel crowned with a battle tank, with a cradle-tight reverse braking device that brakes the return path together and a piston-cylinder unit of the crest gun mount that sets the fire height of the gun barrel;
  • Fig. 2 in a partial enlargement the crest mount of the gun barrel shown in Fig. 1.
  • 3 in a braking force diagram, the braking work of the reverse braking device and the braking means of the piston-cylinder unit and the reduced braking force acting on the shield pin;
  • 4 shows a schematic illustration of the piston-cylinder unit with an electrohydraulic servo valve designed as a braking means;
  • 5 shows a schematic illustration of a pressure-maintaining valve arranged outside the piston-cylinder unit and designed as a braking means;
  • 6 shows a schematic representation of a pressure-holding valve arranged as a braking means and arranged within the piston-cylinder unit.

Die in den Figuren 1 und 2 dargestellte hochschwenkbare Scheitellafettierung für das Waffenrohr 3 eines Kampfpanzers 15 besteht im wesentlichen aus zwei das Waffenrohr 3 beidseitig tragenden Lafettenarmen 5 und zwei die Feuerhöhe h des Waffenrohres 3 einstellenden Kolbenzylindereinheiten 1. Durch die symmetrische Anordnung der Lafettenarme 5 und der Kolbenzylindereinheiten 1 beidseitig des Waffenrohres 3 sind in den gezeichneten Seitenansichten der Scheitellafettierung jeweils nur ein Lafettenarm 5 und eine Kolbenzylindereinheit 1 sichtbar. Die Zylinder 8 beider Kolbenzylindereinheiten 1 sind mit einem um die Achse 21 seitenrichtbaren Teil 16 des Panzerfahrzeuges 22 an den Lagerstellen 17 und die Kolbenstange 10 jeder Kolbenzylindereinheit 1 an jeweils einer Lagerstelle 18 eines Lafettenarmes 5 schwenkbeweglich über Lagerbolzen 17', 18' verbunden.The pivotable crest mount shown in Figures 1 and 2 for the weapon barrel 3 of a main battle tank 15 consists essentially of two gun arms 3 supporting the gun barrel 3 on both sides and two piston cylinder units 1 adjusting the height of fire h of the gun barrel 3. The symmetrical arrangement of the gun arms 5 and Piston cylinder units 1 on both sides of the weapon barrel 3 are only visible in the side views of the crest mount, only one mount arm 5 and one piston cylinder unit 1. The cylinders 8 of both piston-cylinder units 1 are connected to a part 16 of the armored vehicle 22 which can be oriented laterally about the axis 21 at the bearing points 17 and the piston rod 10 of each piston-cylinder unit 1 is pivotably connected to a bearing point 18 of a carriage arm 5 via bearing bolts 17 ', 18'.

Das seitenrichtbare Teil 16 enthält an dem den Lagerstellen 17 entgegengesetzt angeordneten Ende 20 weitere Lagerstellen 19, an welchen jeweils die Lafettenarme 5 über Lagerbolzen 19' hochschwenkbar angeschlossen sind.The side-directional part 16 contains at the end 20 located opposite the bearing points 17 further bearing points 19, to which the carriage arms 5 are connected so that they can be pivoted up via bearing bolts 19 '.

Das Waffenrohr 3 ist innerhalb der Waffenrohrwiege 14 gelagert, wobei es innerhalb der Waffenrohrwiegenlagerung beim Waffenrohrdurchlauf eines Geschosses 23 um einen widerstandsfreien Frailauf d und einen Bremsbereich b einer Rohrrücklaufbremseinrichtung 6, die vorzugsweise auch mit einer nicht dargestellten Vorholeinrichtung ausgerüstet ist, zurück- und vorlaufen kann. Der Rücklauf- und Vorlaufweg (b+d) der Rücklaufbremseinrichtung 6 ist kurz und entspricht vergleichsweise den kurzen Rücklaufwegen bekannter Rücklaufbremseinrichtungen, die ohne die Standfestigkeit bekannter Panzerfahrzeuge zu gefährden, zum Abbremsen eines im Turm eines Kampfpanzers eingesetzten und eine hohe Schussenergie übertragbaren Waffenrohres eingesetzt werden. Derartige, beispielsweise kombinierte Rücklaufbrems- und Rohrvorholeinrichtungen mit Freilauf und kurzem Bremshub sind aus der DE-PS 3 015 097 bekannt.The weapon barrel 3 is mounted within the weapon barrel cradle 14, whereby it can move back and forth within the weapon barrel cradle storage when the weapon barrel passes through a projectile 23 by a resistance-free barrel run d and a braking area b of a barrel return braking device 6, which is preferably also equipped with a recovery device (not shown). The return and forward travel (b + d) of the return braking device 6 is short and corresponds comparatively to the short return travel of known return braking devices, which are used without braking the stability of known armored vehicles, for braking a weapon barrel used in the turret of a main battle tank and for transferring high shot energy. Such, for example, combined return brake and pipe recovery devices with free wheel and short brake stroke are known from DE-PS 3 015 097.

Der Zylinder 24 der Rücklaufbremseinrichtung 6 ist in bekannter Weise fest mit der Waffenrohrwiege 14 verbunden, während ihr Kolben 25 an dem zurück- und vorlaufenden verschlussseitigen Ende 26 des Waffenrohres 3 angeschlossen ist. Die Waffenrohrwiege 14 enthält aussenseitig zur Lagerung in den Lafettenarmen 5 beidseitig angeordnete Schildzapfen 13, um deren Achse das Waffenrohr 3 in einer durch die Kolbenzylindereinheiten 1 hochgeschwenkten Stellung 2 in der Feuerhöhe h durch an jedem Lafettenarm 5 befestigte Höhenrichtzylinder 27 in einem Winkelbereich β höhenrichtbar ist.The cylinder 24 of the return brake device 6 is firmly connected in a known manner to the weapon barrel cradle 14, while its piston 25 is connected to the return and forward end 26 of the weapon barrel 3. The gun barrel cradle 14 contains shield pins 13 arranged on both sides for storage in the carriage arms 5, around the axis of which the gun barrel 3 can be adjusted in height in an angular range β in an angle range β in a position 2 pivoted up by the piston cylinder units 1 at the fire height h by means of height adjustment cylinders 27 attached to each carriage arm 5.

Der Höhenrichtzylinder 27 ist in der Lage, das Waffenrohr 3 derartig zu stabilisieren, dass es bei einer im Winkelbereich ß eingenommenen Feuerstellung 28 während des Rück- und Vorlaufs seine zielgerichtete Lage beibehält. Zum Anvisieren der Ziele enthält der Kampfpanzer des weiteren eine nicht dargestellte Visiereinrichtung. Zum Laden des Waffenrohres 3 ist an der Waffenrohrwiege 14 eine schwenkbewegliche Ladeeinrichtung 29 befestigt, deren Aufbau und Funktion jedoch nicht erfindungswesentlich ist und deshalb nicht weiter erläutert wird.The leveling cylinder 27 is able to stabilize the weapon barrel 3 in such a way that it maintains its targeted position when the firing position 28 is in the angular range β during the return and advance. To target the targets, the main battle tank also contains a sighting device, not shown. For loading the weapon barrel 3, a pivoting loading device 29 is fastened to the weapon barrel cradle 14, the structure and function of which, however, is not essential to the invention and is therefore not explained further.

Die Kolbenzylindereinheit 1 ist in der Lage, den Lafettenarm 5 aus einer am Panzerfahrzeug 22 aufliegenden annähernd horizontalen Ausgangslage in eine fast senkrechte maximale Position hochzuschwenken. Die Lagerung des Waffenrohres 3 befindet sich in der Ausgangslage des Lafettenarmes 5 in einer der untersten Feuerhöhe h' entsprechenden Ausgangsstellung 30. Bei einer vergleichsweise flachen und einen nur geringen Neigungswinkel von y kleiner 30° aufweisenden Einbaulage der Kolbenzylindereinheit 1 ist zum Aufschwenken des Lafettenarmes 5 nur ein geringer raumsparender Kolbenhub e der Kolbenstange 10 erforderlich. Während des Hubes e bewegt sich die Lagestelle 18 derartig auf einem kreisförmigen Weg 31 um die Lagerstelle 19, dass die Schräglage der Kolbenzylindereinheit 1 nur unwesentlich verändert wird.The piston-cylinder unit 1 is able to pivot the carriage arm 5 from an approximately horizontal starting position lying on the armored vehicle 22 into an almost vertical maximum position. The storage of the gun barrel 3 be can be found in the starting position of the carriage arm 5 in a starting position 30 corresponding to the lowest fire height h '. With a comparatively flat and only a slight inclination angle of y less than 30 °, the piston-cylinder unit 1 is only a small space-saving piston stroke e for pivoting the carriage arm 5 the piston rod 10 required. During the stroke e, the position 18 moves in a circular path 31 around the bearing 19 such that the inclined position of the piston-cylinder unit 1 is changed only insignificantly.

Jeder Kolbenzylindereinheit 1 ist ein in den Figuren 4 bis 6 dargestelltes Bremsmittel 4 und eine Steuereinheit 33 zugeordnet. Das Bremsmittel 4 erfüllt den Zweck, in einem Rücklaufbereich a der Schildzapfen 13 und somit auch des Waffenrohres 3, die rückwärtige Schwenkbewegung des Lafettenarmes 5 in einem Winkelbereich a, für die Rücklaufenergieentlastung des Waffenrohres 3 und der mit dem Waffenrohr 3 zurücklaufenden Massen nutzbar zu machen. Das Bremsmittel 4 ist in jeder hochgeschwenkten Stellung 2 des Waffenrohres 3 bei der Schussabgabe wirksam, wodurch beim Rohrrücklauf nach beendetem Freilauf d der Rohrrücklaufbremseinrichtung 6 innerhalb eines aus den Rohrrücklaufbereichen (a + b) gemeinsam gebildeten Rohrrücklaufweges c die Rücklaufenergie des Waffenrohres 3, des Verschlusses 32 und weiterer mit dem Waffenrohr 3 zurücklaufenden Massen, gleichzeitig einerseits durch die Kolbenzylindereinheit 1 über den dem Rohrrücklaufbereich a entsprechend um den Winkel a zurückgeschwenkten Lafettenarm 5 und andererseits durch die wiegenfeste um den Bereich b zurückgelaufene Rohrrücklaufbremseinrichtung 6 energieverzehrend absorbiert wird.Each piston-cylinder unit 1 is assigned a braking means 4 shown in FIGS. 4 to 6 and a control unit 33. The braking means 4 serves the purpose of making the rearward pivoting movement of the carriage arm 5 in an angular range a in a return region a of the shield pins 13 and thus also of the weapon barrel 3 usable for the return energy relief of the weapon barrel 3 and the masses returning with the weapon barrel 3. The braking means 4 is effective in every swiveled-up position 2 of the weapon barrel 3 when firing the shot, so that when the barrel returns after free running d of the barrel return braking device 6, the return energy of the barrel 3, of the breech 32 within a barrel return path c formed from the barrel return regions (a + b) and further masses returning with the weapon barrel 3, at the same time being absorbed in an energy-consuming manner by the piston-cylinder unit 1 via the carriage arm 5 pivoted back by the angle a corresponding to the barrel return area a and on the other hand by the tube-fixed barrel return brake device 6 which has returned to the area b.

Dadurch wird, wie es das Diagramm gemäss Fig. 3 zeigt, die am Schildzapfen 13 wirkende Bremskraft F derartig reduziert, dass eine ausreichende Standsicherheit des Panzerfahrzeuges 22 bei Schusshöhen h grösser 4 m beim Einsatz üblicherweise im Turm eines Kampfpanzers einsetzbarer und eine hohe Schussenergie übertragbarer Waffenrohre 3 besteht. Auf diese Weise können bei stabiler Standsicherheit des Panzerfahrzeuges 22 Feuerhöhen h bis zu 8 m erreicht werden.As a result, as the diagram according to FIG. 3 shows, the braking force F acting on the shield pin 13 is reduced in such a way that sufficient armor vehicle 22 stability at shot heights h greater than 4 m when used is typically used in the turret of a main battle tank and high shot energy transferable weapon barrels 3 exists. In this way, 22 fire heights h up to 8 m can be achieved with stable armor vehicle stability.

Bei der geringsten Feuerhöhe h' wird das Waffenrohr 3 in der Ausgangsstellung 30 ausschliesslich in bekannter Weise durch die Rücklaufbremseinrichtung 6 innerhalb des Rücklaufbereichs b gebremst, weil die Kolbenstange 10 ihre in den Zylinder 8 hineingeschobene Endposition 34 erreicht hat und ein Weiterschwenken des Lafettenarmes 5 nicht möglich ist. Aufgrund des geringen Bremsbereichs b ist die am Schildzapfen 13 wirkende Bremskraft F1 vergleichsweise gross, wobei jedoch aufgrund der geringen Feuerhöhe h' die Standsicherheit des Panzerfahrzeuges 22 nicht gefährdet ist.At the lowest firing height h ', in the starting position 30, the weapon barrel 3 is braked exclusively in a known manner by the return brake device 6 within the return region b, because the piston rod 10 has reached its end position 34 pushed into the cylinder 8 and pivoting of the carriage arm 5 is not possible is. Due to the small braking area b, the braking force F 1 acting on the shield pin 13 is comparatively large, but the stability of the armored vehicle 22 is not endangered due to the low fire height h '.

Die Bremsarbeit A1 der Rücklaufbremseinrichtung 6 entspricht dabei dem Produkt aus der Kraft F1 x Bremsbereich b und somit der durch die Punkte A, B, C, D eingeschlossenen Rechteckfläche.The braking work A 1 of the return braking device 6 corresponds to the product of the force F 1 x braking area b and thus the rectangular area enclosed by the points A, B, C, D.

Bei grossen Feuerhöhen h, vorzugsweise über 4 m, bei denen ein aus den Rücklaufbremsbereichen (a + b) bestehender maximaler Rücklaufweg c möglich ist, wirkt bei der gleichen dem Produkt F, x b entsprechenden Bremsarbeit A2 = A, am Schildzapfen 13 eine im Verhältnis der Bremswegverlängerung reduzierte Bremskraft F2 = F, x b/(a + b).At large fire heights h, preferably over 4 m, in which a maximum return path c consisting of the return braking areas (a + b) is possible, the same applies to the same braking work A 2 = A, corresponding to the product F, xb, on the shield pin 13 the braking distance extension reduced braking force F 2 = F, xb / (a + b).

Das Bremsmittel 4der Kolbenzylindereinheit 1 und die hydraulische Dämpfung der Rücklaufbremseinrichtung 6 sind während der gleichzeitig ablaufenden Bremsvorgänge beider Bremseinrichtungen 4, 6 derartig aufeinander abgestimmt, dass die am Schildzapfen 13 der Waffenrohrwiege 14 wirkende Bremskraft F2 innerhalb des Rohrrücklaufweges c annähernd konstant ist. Entsprechend den Bremswegen a bzw. b entspricht die vom Bremsmittel 4 verrichtete Bremsarbeit dem Produkt F2 x a und somit der von den Punkten B, E, F, G eingeschlossenen Rechteckfläche und die von der Rücklaufbremseinrichtung 6 verrichtete Bremsarbeit dem Produkt F2 x b und somit der von den Punkten A, B, G, H eingeschlossenen Rechteckfläche. Die gesamte Bremsarbeit Az entspricht somit der von den Punkten A, E, F, H eingeschlossenen Rechteckfläche.The braking means 4 of the piston-cylinder unit 1 and the hydraulic damping of the return brake device 6 are coordinated with one another during the simultaneous braking processes of the two brake devices 4, 6 such that the braking force F 2 acting on the shield pin 13 of the gun barrel cradle 14 is approximately constant within the tube return path c. Corresponding to the braking distances a and b, the braking work performed by the braking means 4 corresponds to the product F 2 xa and thus the rectangular area enclosed by the points B, E, F, G and the braking work performed by the return braking device 6 corresponds to the product F 2 xb and thus the Rectangular area enclosed by points A, B, G, H. The total braking work A z thus corresponds to the rectangular area enclosed by the points A, E, F, H.

Bei kleiner werdenden Feuerhöhen h, vor allem unterhalb 4 m, nimmt im unteren Schwenkbereich des Lafettenarmes 5 der horizontale Rücklaufbereich a des Schildzapfens 13 und somit des Waffenrohres 3 zunehmend kleiner werdend ab. Deshalb steigt bei gleicher Bremsbarkeit Az und kleiner werdenden Bremsbereichen a des Bremsmittels 4 die Bremskraft über einen die Bremskraft F2 übersteigenden Betrag an, bis sie bei der Feuerhöhe h' wieder den Betrag der Bremskraft F, erreicht hat.As the fire heights h decrease, especially below 4 m, the horizontal return area a of the shield pin 13 and thus of the weapon barrel 3 decreases progressively smaller in the lower pivoting range of the carriage arm 5. Therefore, with the same braking ability A z and decreasing braking areas a of the braking means 4, the braking force increases by an amount exceeding the braking force F 2 until it has reached the amount of the braking force F again at the height of fire h '.

Das Bremsmittel 4 ist mit einem während des Rohrrücklaufs Hydraulikmedium verdrängenden Zylinderraum 7, 7' des zur Kolbenzylindereinheit 1 gehörenden Zylinders 8 verbunden und kann innerhalb des Zylinders 8 oder ausgangsseitig des Zylinderraumes 7 ausserhalb des Zylinders 8 angeordnet sein. Neben dem Zylinderraum 7, 7' erzeugt ein an der Kolbenstange 10 befestigter innerhalb des Zylinders 8 gleitbarer Kolben 42 einen weiteren zur beidseitigen Bewegung der Kolbenstange 10 notwendigen Zylinderraum 43, 43'.The brake means 4 is connected to a cylinder space 7, 7 ′ of the cylinder 8 belonging to the piston-cylinder unit 1, which displaces hydraulic medium during the pipe return and can be arranged inside the cylinder 8 or on the output side of the cylinder space 7 outside the cylinder 8. In addition to the cylinder space 7, 7 ', a piston 42 which is slidable within the cylinder 8 and which is fastened to the piston rod 10 produces a further cylinder space 43, 43' which is necessary for moving the piston rod 10 on both sides.

Bei der Anordnung ausserhalb des Zylinders 8 ist das Bremsmittel 4 gemäss Fig. 4 und 5 innerhalb einer Steuereinheit 33 integriert.With the arrangement outside the cylinder 8, the braking means 4 according to FIGS. 4 and 5 is integrated within a control unit 33.

Entsprechend Fig. 4 ist das Bremsmittel 4 ein elektrohydraulisches Servoventil 11, dessen Durchflussquerschnitt 36 zur Erzielung eines annähernd konstanten Bremskraftverlaufs 12 (Fig. 3) wegabhängig von der sich während des Rohrstücklaufs zurückbewegenden Kolbenstange 10 der Kolbenzylindereinheit 1 über einen Steuergliedverstärker 37 und druckabhängig von dem in der Rücklaufbremseinrichtung 6 entstehenden Bremsdruck über einen mit dem Steuergliedverstärker 37 verbundenen Druckgeber 35 drosselbar ist. Während des Bremsvorganges ist der Zylinderraum 7 über eine Leitung 44 mit dem drosselbaren Durchflussquerschnitt 36 und der Zylinderraum 43 über eine Leitung 45 mit einer nicht dargestellten hydraulischen Energiequelle verbunden, wobei der Durchflussquerschnitt in den Zylinderraum 43 ebenfalls gedrosselt ist.4, the braking means 4 is an electrohydraulic servo valve 11, the flow cross section 36 of which, in order to achieve an approximately constant braking force profile 12 (FIG. 3), is path-dependent from the piston rod 10 of the piston-cylinder unit 1 moving back during the pipe run, via a control element amplifier 37 and pressure-dependent from the of the return brake device 6 can be throttled brake pressure via a pressure transmitter 35 connected to the control element amplifier 37. During the braking process, the cylinder space 7 is connected via a line 44 to the throttled flow cross section 36 and the cylinder space 43 via a line 45 to a hydraulic energy source (not shown), the flow cross section into the cylinder space 43 also being throttled.

Nach beendetem Bremsbereich a ist das Servoventil 11 in der Schaltstellung 38 in der Lage, die Kolbenstange 10 in die Richtung 39 vorwärts zu bewegen, wodurch auch der Lafettenarm 5 (Fig. 1) den Schildzapfen 13 wieder in die Stellung 2 vorwärts bewegt. In der Schaltstellung 40 ist eine Veränderung der Stellung 2 (Fig. 1) nicht möglich, während in der Schaltstellung 41 die Kolbenstange 10 in entgegengesetzter Richtung 39 zurückbewegbar ist und somit geringe Feuerhöhen h einstellbar sind.After the braking region a has ended, the servo valve 11 in the switching position 38 is able to move the piston rod 10 forward in the direction 39. whereby the carriage arm 5 (Fig. 1) moves the shield pin 13 back to position 2 forward. In the switching position 40, a change in the position 2 (FIG. 1) is not possible, while in the switching position 41 the piston rod 10 can be moved back in the opposite direction 39 and thus small fire heights h can be set.

Gemäss Fig. 5 ist das Bremsmittel 4 als ein Druckhalteventil 9 ausgebildet, das innerhalb der Steuereinheit 33 während des Rohrrücklaufbereichs a mit einem nicht drosselnden 4/4 Wegeventil 46 verbunden ist. Dadurch ist ebenfalls während des Bremsvorganges eine vorgebbare konstante Bremskraft erzeugbar. Die zum Verstellen der Feuerhöhe h notwendigen Schaltstellungen 38, 40, 41 entsprechen den bereits beschriebenen Schaltstellungen gemäss Fig. 4.5, the brake means 4 is designed as a pressure-maintaining valve 9, which is connected to a non-throttling 4/4 way valve 46 within the control unit 33 during the pipe return region a. As a result, a predeterminable constant braking force can also be generated during the braking process. The switch positions 38, 40, 41 required to adjust the fire height h correspond to the switch positions already described according to FIG. 4.

Fig. 6 verdeutlicht die Anordnung eines als Druckhalteventil 9' ausgebildeten Bremsmittels 4 innerhalb des Kolbens 42. Dadurch, dass der Ventilkegel 47 erst nach Überwindung eines vorgebbaren Druckes innerhalb des Zylinderraumes 78 öffnet, ist unter Einhaltung einer konstanten Bremskraft eine Bremsbewegung der Kolbenstange 10 innerhalb des Zylinders 8 möglich. Während des Bremsvorganges ist die Leitung 44' des Kolbenraumes 7' verschlossen. Zum Verstellen der Feuerhöhe h (Fig. 1) wird für diese Anordnung ein 4/3 Wegeventil 48 mit den weiteren vorbeschriebenen Schaltstellungen 38, 41 innerhalb der Steuereinheit 33 benötigt.Fig. 6 illustrates the arrangement of a brake means 4 designed as a pressure-maintaining valve 9 'within the piston 42. Because the valve cone 47 only opens after a predetermined pressure has been overcome within the cylinder space 78, a braking movement of the piston rod 10 within the piston is maintained while maintaining a constant braking force Cylinder 8 possible. During the braking process, the line 44 'of the piston chamber 7' is closed. To adjust the fire height h (FIG. 1), a 4/3 directional control valve 48 with the other switching positions 38, 41 described above within the control unit 33 is required for this arrangement.

Die in den Figuren 4 bis 6 gezeichneten Schaltzeichen entsprechen der internationalen Norm ISO 1219.The circuit symbols drawn in FIGS. 4 to 6 correspond to the international standard ISO 1219.

Nach einem nicht dargestellten Ausführungsbeispiel ist es des weiteren möglich, die Scheitellafettierung nur mit einer Kolbenzylindereinheit 1 und einem dazugehörigen Bremsmittel 4 auszustatten. Dementsprechend wird für die Höhenverstellung des Waffenrohres 3 ebenfalls nur ein Lafettenarm 5 benötigt, der sich jedoch zur beidseitigen Befestigung des Waffenrohres 3 im Bereich der Schildzapfen 13 aufgabelt.According to an embodiment, not shown, it is further possible to equip the crown mount only with a piston-cylinder unit 1 and an associated brake means 4. Accordingly, only one carriage arm 5 is also required for the height adjustment of the weapon barrel 3, which, however, bifurcates in the region of the shield pins 13 for fastening the weapon barrel 3 on both sides.

Claims (4)

1. Lifting gun mount for the gun barrel (3) of a battle tank (15) with at least one piston cylinder unit (1) which is to be set for the firing height (h) of the barrel (3) and which is pivotably connected at the cylinder end with the elevation part (16) of the tank structure (22) and at its piston end (20) with a gun mount arm (5) bearing the weapon, and with a barrel recoil braking device (6) which is affixed to the barrel cradle and which has a free-running device (d) to enable the barrel to return without resistance while the projectile (23) is passing through the barrel, characterised by the fact that the piston cylinder unit (1) required for setting the firing height (h) of the gun barrel 3 has a braking means (4) which, in any position (2) to which the barrel (3) has been pivoted upwards, takes effect on the firing action in such a way that the braking force (F) formed from the recoil braking device (6) and the braking means (4) of the piston cylinder unit (1) and acting on the trunnion (13) of the barrel cradle (14) is approximately constant during the braking process within the path (c) of the return of the barrel, while in the said return of the barrel, after completion of the free-running action (d) of the barrel recoil braking device (6), within a barrel return path (c) formed from the barrel return zones (a) and (b) in common, the return energy of the gun barrel (3) and of the mass returning with the gun barrel (3) is absorbed simultaneously and with consumption of energy, on the one hand by the piston cylinder unit (1) through the gun mount arm (5) pivoted back by an angle a in accordance with the barrel return zone (a) and on the other hand by the barrel recoil braking device (6) which is integral with the cradle and which has moved back by the zone (b).
2. Gun mount in accordance with Claim 1, characterised by the following features:
a) the braking means (4) is connected with a cylinder chamber (7) belonging to the piston cylinder unit (1) and displacing hydraulic medium during the return movement of the barrel, and
b) it is positioned on the output side of the cylinder chamber (7) outside the cylinder (8) of the piston cylinder unit (1) or inside the cylinder (8).
3. Gun mount in accordance with Claims 1 and 2, characterised by the fact that the braking means (4) consists of a pressure-holding valve (9, 9').
4. Gun mount in accordance with Claims 1 and 2, characterised by the fact that the braking means (4) consists of an electro-hydraulic servo-valve (11), of which the flow cross section (36), in order to obtain the approximately constant brake force pattern (12) can be throttled in accordance with the path covered by the piston rod (10) of the piston cylinder unit (1) and moving back during the return movement of the barrel, in accordance with the brake pressure occurring the recoil braking device (6).
EP85113164A 1984-11-02 1985-10-17 Lifting gun mount for battle tanks Expired EP0185871B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3440041 1984-11-02
DE3440041A DE3440041A1 (en) 1984-11-02 1984-11-02 HIGH-SWIVEL HEAD Grease for the weapon barrel of a battle tank

Publications (2)

Publication Number Publication Date
EP0185871A1 EP0185871A1 (en) 1986-07-02
EP0185871B1 true EP0185871B1 (en) 1988-04-20

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP85113164A Expired EP0185871B1 (en) 1984-11-02 1985-10-17 Lifting gun mount for battle tanks

Country Status (3)

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US (1) US4706543A (en)
EP (1) EP0185871B1 (en)
DE (2) DE3440041A1 (en)

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DE3440041A1 (en) 1986-05-07
US4706543A (en) 1987-11-17
EP0185871A1 (en) 1986-07-02
DE3562300D1 (en) 1988-05-26

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