EP0185871A1 - Lifting gun mount for battle tanks - Google Patents

Abstract

A piston-cylinder unit 1 of a pivotable crest mount, which is required to set the fire height of the weapon barrel 3 of a main battle tank, contains a braking agent which is effective in each raised position 2 of the weapon barrel 3 when the shot is fired. This makes it possible to make the pivoting movement of a gun arm 3 carrying the gun barrel 3 usable for the return energy relief of the gun barrel 3. In the case of barrel return, after free running d of a known barrel return braking device 6, the barrel return energy of the weapon barrel 3 and the masses returning with the barrel 3 are simultaneously within a barrel return path c formed from the return regions a and b, on the one hand by the piston-cylinder unit 1, via the the carriage arm 5 pivoted back by an angle α corresponding to the pipe return area a and, on the other hand, is absorbed in an energy-consuming manner by the return brake device 6 which has run back a comparatively short area b and which is fixed against the cradle. As a result, known weapon tubes 3, which can be used in armored turrets, and short-term reverse braking devices 6 with freewheeling d can be used, saving weight and manufacturing effort. nevertheless, at fire heights greater than 4 m, a long return path which does not endanger the stability of the armored vehicle for braking the weapon barrel 3 is ensured.

Description

The invention relates to a swiveling crest mount for the weapon barrel of a main battle tank according to the preamble of claim 1.

Such crest mountings are known and are described, for example, in US Pat. No. 4,326,446.

When using these crest mountings, it is necessary to achieve a sufficient stability of the main battle tank vehicle with comparatively large fire heights greater than 4 m, to increase the braking distance of the tube returning when the shot is fired by a multiple compared to a weapon barrel carrying a high shot energy transfer in the tank 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.

However, such long weapon barrel bearings and barrel brake and barrel recovery devices disadvantageously have a high weight and cause a not insignificant manufacturing outlay.

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 manufacturing costs are saved, the gun barrel usually used in a turret of the main battle tank and the associated, known per se a short return path generating a high return energy preferably combined pipe return brake and recuperation device can be used in a crest mount of a battle tank with a fire height greater than 4 m without endangering the stability of the battle tank when firing the shot.

This object is achieved by the invention specified in claim 1. The subclaims name advantageous refinements and developments.

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-stroke, 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 a particularly advantageous manner, when the shot is fired, the entire 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 oc by 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.

Because of this, in addition to the cradle-proof return brake device, the pipe return can also be braked by means of the braking means of the piston-cylinder unit, 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 possibility of pivoting the carriage arm back.

Depending on the amount of braking energy, on the one hand the return braking device and on the other hand the braking means of the piston-cylinder unit, the braking areas a of the braking means and b of the return braking device can be adjusted to one another in such a way that the return travel 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 small pipe return length within the cradle bearing and comparatively small structural units for the return braking device, with the possibility of even at high fire heights Reduce the braking area b in such a way that the braking area a corresponds approximately to the maximum pipe return path c.

With comparatively small braking area lengths b of known reverse braking devices and at fire heights: 7 4 m and braking area lengths a / b = 2/1, the armored vehicle can be adequately stable 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 5.5 m and a braking area ratio a / b = 2/1, a reduction in the stability of the armored vehicle guaranteeing the stability of the armored vehicle from 600 kN to 200 kN is achieved.

Characterized in that the braking means can be designed as a pressure-maintaining valve or as an electro-hydraulic servo valve, the throttle cross section of the servo valve depending on the path moving back during the pipe return Piston rod of the piston cylinder unit and pressure-dependent can be controlled by the brake pressure generated in the return brake device, the braking force can advantageously be kept approximately constant over the entire pipe return path, the reduced braking force having a gentle effect on the mounting, the return brake device and the piston cylinder unit.

The invention is explained in more detail with reference to the exemplary embodiments shown in the drawings.

• 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;

It shows:

• 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 of 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-maintaining valve arranged as a braking means and arranged within 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 freewheeling 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 brake device 6 is short and corresponds comparatively to the short return because of known reverse braking devices which are used without endangering the stability of known armored vehicles, for braking a weapon barrel used in the turret of a main battle tank and a high shot energy transfer. Such, for example, combined return brake and pipe recovery devices with free wheel and short brake stroke are known from DE-PS 30 15 097.

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 barrel 9 of the weapon barrel. The gun barrel cradle 14 contains on the outside for storage in the carriage arms 5 shield pins 13 arranged on both sides, around the axis of which the gun barrel 3 can be adjusted in height in an angular range P in a position 2 pivoted up by the piston-cylinder units 1 at the firing height h by height-adjusting 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 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.

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 weapon barrel 3 is in the starting position of the carriage arm 5 in a starting position 30 corresponding to the lowest fire height h ' Flat and only a small angle of inclination of less than 30 °, installation position of the piston-cylinder unit 1, only a small, space-saving piston stroke e of the piston rod 10 is required to swing open the carriage arm 5. During the stroke e, the bearing point 18 moves in a circular path 31 around the bearing point 19 such that the inclined position of the piston-cylinder unit 1 is only slightly changed.

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 o (, for the return energy relief of the gun barrel 3 and the masses returning with the gun barrel 3) usable in a return area a of the shield pins 13 and thus also of the gun 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 within a barrel return path formed from the barrel return regions (a + b), the return energy of the barrel 3, the breech 32 and other masses returning with the weapon barrel 3, at the same time, on the one hand, by the piston-cylinder unit 1 via the barrel return area a correspondingly pivoted back by the angle α by the carriage arm 5 and on the other hand by the cradle-proof barrel return brake device 6 which has returned to the area b nd is absorbed.

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 adequate stability of the armored vehicle 22 at shot heights h greater than 4 m is typically used in the turret of a main battle tank rer and a high shot energy transferable gun barrels 3 exists. In this way, 22 fire heights h of up to 8 m can be achieved with a stable stability of the armored vehicle.

At the lowest fire height h ', the gun barrel 3 in the starting position 30 is braked exclusively in a known manner by the return brake device 6 within the return area 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.

At large fire heights h, preferably over 4 m, at 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 ₁ on the shield pin 13 corresponding to the product F ₁ xb the run Bremswegverlänge- ^g reduced braking force F ₂ = F ₁ x b / (a + b).

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 both 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 points B, E, F, G and the braking work performed by the return braking device 6, the product F ₂ xb and thus the rectangular area enclosed by points A,, B, G, H. The total braking work A ₂ thus corresponds to the rectangular area enclosed by the points A, E, F, H.

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 work A ₂ 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 ₁ 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. 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.

In the arrangement outside the cylinder 8, the braking means 4 according to FIGS. 4 and 5 is integrated within a control unit 33.

4, the braking means 4 is an electrohydraulic servo valve 11, the flow cross section 36 of which is dependent on the path to achieve an approximately constant braking force profile 12 (FIG. 3) during the process of the pipe return moving piston rod 10 of the piston-cylinder unit 1 can be throttled via a control element booster 37 and, depending on the pressure, from the brake pressure generated in the return brake device 6 via a pressure transmitter 35 connected to the control element booster 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.

After the braking area 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, as a result of which the carriage arm 5 (FIG. 1) also moves the shield pin 13 back into the position 2. 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.

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 illustrates the arrangement of a brake means 4 designed as a pressure maintaining valve 9 'within the piston 42. The fact that the valve cone 47 opens only after a predetermined pressure has been overcome within the cylinder space 7 is maintained while maintaining a constant

Braking force a braking movement of the piston rod 10 within the cylinder 8 is 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.

The circuit symbols drawn in FIGS. 4 to 6 correspond to the international standard ISO 1219.

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.

Reference symbol list

• 1 piston-cylinder unit
• 2 position
• 3 gun barrel
• 4 brake means
• 5 carriage arm
• 6 reverse braking device
• 7 cylinder space
• 7 'cylinder space
• 8 cylinders
• 9 pressure valve
• 9 'pressure valve
• 10 piston rod
• 11 valve
• 12 braking force curve
• 13 shield pins
• 14 gun barrel cradle
• 15 main battle tanks
• 16 part
• 17 depository
• 17 'bearing pin
• 18 depository
• 18 'bearing pin
• 19 depository
• 19 'bearing pin
• 20 end
• 21 axis
• 22 armored vehicle
• 23 floor
• 24 cylinders
• 25 pistons
• 26 end
• 27 leveling cylinders
• 28 Firing position
• 29 loading device
• 30 Starting position
• 31 way
• 32 closure
• 33 control unit
• 34 end position
• 35 pressure sensors
• 36 flow cross-section
• 37 control amplifier
• 38 switch position
• 39 direction
• 40 switch position
• 41 switch position
• 42 pistons
• 43 cylinder space
• 44 line
• 44 'line
• 45 line
• 46 directional control valve
• 47 valve cone
• 48 way valve
• a return area
• b Return area
• c pipe return path
• d freewheel
• e hub
• h height of fire
• h 'fire height
• ^A _{l B} rem work
• A ₂ braking work
• F ₁ braking force
• F2 braking force
• α angle
• β angular range
• γ angle of inclination

Claims (5)

1. Swiveling crest mount for the weapon barrel of a battle tank with at least one piston-cylinder unit that adjusts the fire height of the weapon barrel, which is pivotally connected at its cylinder-side end to the side-directional part of the armored vehicle and at its piston-side end to a gun arm carrying the weapon, and to one on the Gun barrel cradle attached tube return brake device, which has a freewheel for a resistance-free tube return during the gun barrel passage of the projectile, characterized in that the piston-cylinder unit (1) required for adjusting the fire height (h) of the gun barrel (3) contains a braking means (4), which in each the swiveled-up position (2) of the weapon barrel (3) becomes effective when the shot is fired, so that when the barrel returns, after free running (d) of the barrel return braking device (6), within a barrel return path (c) formed jointly from the barrel return areas (a) and (b) the return energy of the weapon barrel (3) and the masses returning with the weapon barrel (3) simultaneously, on the one hand through the piston-cylinder unit (1) via the corresponding to the pipe return area (a), the carriage arm (5) pivoted back by an angle α and, on the other hand, is absorbed in an energy-consuming manner by the pipe return brake device (6) which is fixed to the cradle and has returned to area (b). 2. crown mount according to claim 1, characterized in that from the return brake device (6) and the braking means (4) of the piston-cylinder unit (1) formed on the shield pin (13) of the gun barrel cradle ( ₁ 4) acting braking force (F) during the braking process within the pipe return path (c) is approximately constant. 3. crest mount according to claim 1 and 2, characterized by the following features: a) the brake means (4) is connected to a cylinder chamber (7) of the piston-cylinder unit (1) which displaces hydraulic medium during the pipe return and b) it is arranged on the output side of the cylinder space (7) outside the cylinder (8) of the piston-cylinder unit (1) or inside the cylinder (8). 4. crest mount according to one of claims 1 to 3, characterized in that the braking means (4) is a pressure maintaining valve (9, 9 '). 5. crown mount according to one of claims 1 to 3, characterized in that the braking means (4) is an electrohydraulic servo valve (11), the flow cross section (36) for achieving the approximately constant braking force curve (12) can be throttled depending on the piston rod (10) of the piston-cylinder unit (1) moving back during the pipe return and pressure-dependent on the braking pressure arising in the return braking device ( ₆ ).

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