EP0160735B1 - Velocity simulator for monitoring the recoiling and returning parts of a large-calibre weapon barrel - Google Patents

Description

The invention relates to a speed simulator according to the preamble of patent claim 1.

From DE-B-1 948 613 it is known for production engineering checks of a large-caliber weapon barrel, for example to control the locking movements and the loading process, to slowly retract the barrel with the parts returning and firing when the shot is fired with the aid of a chain or cable pull in order to then by mechanically disengaging the chain or cable hoist to achieve a fast and with the same forward speed as when firing the pipe advance. In addition to the risk of injury due to the sudden relaxation of the chain or cable hoist during the release process, it is difficult to install the chain or cable hoist in cramped pipe return spaces, especially in self-propelled howitzers. Furthermore, with the chain or cable hoist, no slow or variable pipe advance can be achieved. Above all, the return and advance movements of a large-caliber weapon barrel cannot be interrupted to check and adjust the breech functions and the loading device on the weapon side, especially not at maximum forward speed, the so-called "cold shot".

From GB-A-1 259 044 a speed simulator according to the preamble of claim 1 is known, which has the particular purpose of testing the retracting mechanism of the barrel. This simulator essentially consists of a piston-cylinder unit, the piston of which is connected on one side to a piston rod and can be acted upon by hydraulic medium and on the other side closes off a gas space within which the gas can be compressed by the oil supply. The hydraulic medium can be drained through a valve connected to the hydraulic chamber of the piston-cylinder unit, so that the piston and thus also the piston rod can be suddenly moved back by the expanding gas volume. This movement is used to simulate the gun barrel return movement, which means that it is necessary to attach this simulator to the mouth of the gun barrel and to place a counter bearing stationary outside an armored vehicle to support the considerable pressure loads. Due to this arrangement, which requires a considerable installation length, and the structure and the mode of operation, this simulator cannot be installed manually in a narrow installation space inside a turret behind the weapon barrel, especially not because the weapon barrel at the rear end has to be pulled back and not pushed back and because with the known device no variation of the forward speed, in particular up to the maximum forward speed and any interruption of the rewind and fast forward can be simulated.

In contrast, it is an object of the invention to provide a speed simulator by means of which the control movements of the pipe return and pipe flow can be varied in speed and any and safe interruption of the control movements is possible, especially also during the maximum flow speed. Furthermore, the speed simulator should be portable and can be installed in narrow tube return spaces, preferably in the turret of a self-propelled howitzer.

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

The invention is advantageously characterized in that a manually portable, hydraulically operated control and piston unit that can be installed both in cramped pipe return spaces and that can be used by mobile repair groups in the field and that can be operated safely, is provided, which is easily connected to a pressure supply, preferably to a, by means of quick-action couplings A permanently installed hydraulic pressure supply can be connected in the tower of a self-propelled howitzer.

The return and forward speed of the weapon barrel can be adjusted particularly advantageously by means of two throttle valves integrated in the control and piston unit. By means of a switching valve of the control and piston unit, the retractable weapon barrel can be held in any position during forward or return, which further advantageously makes it possible to check and adjust movements on the barrel weapon and on a weapon-side loading device.

Due to the arrangement of a 2/2-way valve known per se in the piston rod, which is designed as a differential piston and works during the return and slow advance, the hydraulic medium is able during the fast advance, largely without resistance, from the cylinder space of the piston rod into the cylinder space of the Flow differential piston. Because the differential piston is arranged at the end of the piston rod inside the hydraulic cylinder, only small inflow cross-sections to the cylinder space of the differential piston are required in accordance with the relatively small amount of residual liquid required for the piston rod cross section times the lead length. The one-sided arrangement of the piston rod also allows a construction of the control and piston-cylinder unit with a short length less than twice the piston stroke, which means that it can be installed in narrow pipe return spaces with a minimum distance corresponding to the length, for example between one Bottom piece of a returned gun barrel and a turret ring is possible.

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

• Fig. 1 in einer schematischen Schnittdarstellung eines gepanzerten Turmes einer großkalibrigen Rohrwaffe die Anordnung eines Geschwindigkeitssimulators an einem Bodenstück eines rück- und vorlaufenden Waffenrohres und an einem Turmkranz ;
• Fig. 2 schematisch die Steuer- und Kolbenzylindereinheit des Geschwindigkeitssimulators in der Schaltstellung « Halt - ;
• Fig. 3 schematisch die Steuer- und Kolbenzylindereinheit in der Schaltstellung « langsamer Rücklauf » ;
• Fig. 4 schematisch die Steuer- und Kolbenzylindereinheit in der Schaltstellung « schneller Vorlauf » ;
• Fig. 5 schematisch die Steuer- und Kolbenzylindereinheit in der Schaltstellung « langsamer Vorlauf ».

It shows :

• Figure 1 is a schematic sectional view of an armored turret of a large-caliber barrel weapon, the arrangement of a speed simulator on a base of a return and forward weapon barrel and on a turret ring.
• Fig. 2 shows schematically the control and piston-cylinder unit of the speed simulator in the switch position «Halt -;
• 3 schematically shows the control and piston-cylinder unit in the “slow return” switch position;
• 4 schematically shows the control and piston-cylinder unit in the “fast forward” switch position;
• Fig. 5 shows schematically the control and piston cylinder unit in the switch position "slow forward".

2-5 show the control elements according to ISO 1219. Fig. 1 illustrates the arrangement of a speed simulator 1 within a turret 48 rotatable in the azimuth plane of a large-caliber tank howitzer between a part 8 returning and advancing with the weapon barrel 11, preferably the base piece 13 and a weapon-fixed bearing 5, preferably arranged on the turret rim 6 Speed simulator 1 consists of a control unit 2 and cylinder unit 3, which are connected to one another in a block construction, with a piston rod 7 protruding from the cylinder 4 on one side at the end 22 (FIG. 2) the bottom piece 13 arranged bearing 50 connected, while the piston rod 7 opposite end 21 of the cylinder 4 (FIG. 2) is also releasably connected to the bearing 5 of the tower ring 6 via a bolt 49.

The control unit 2 and the cylinder unit 3 can be connected in a simple manner via two quick-action couplings 30 directly to supply connections of a hydraulic pressure supply that are not permanently installed within the tower 48. It is constructed in such a way that, against the force acting in the direction 12 (FIG. 2) of a tube retractor arranged in the cradle tube 51 but not shown, a weapon tube 11 pivoted into an index position 51 about the shield pin axis 52 corresponds to the schematic shown in FIGS Switching positions for checking the function of the returning and advancing parts 8 and a loading device, not shown, can be retracted at different return speeds and can be advanced slowly or at the maximum forward speed that occurs when the shot is fired, and the movement sequences can be safely interrupted in any position within the barrel length I ₁ . The speed simulator 1, when the piston rod 7 is retracted by the stroke h, has such a short installation length 1 ₃ that it remains in narrow pipe return spaces 41 with a residual distance ₁ remaining between the base piece 13 and the turret ring 6 with a gun barrel 11 which has returned by the pipe return length I 1 ₂ smaller than two tube return lengths I ₁ or two piston stroke lengths h can be installed in index position 53 on the weapon barrel axis 55, which is extended beyond the base piece 13. The arrangement of the speed simulator 1 on the extended weapon barrel axis 55 does not impede the functional sequence of the weapon, in particular the breech, not shown, and the loading device, also not shown, so that a loading process can be carried out from the barrel.

The structure and the mode of operation of the projectile simulator 1 are described in more detail with reference to FIGS. 2 to 5.

2, the piston-cylinder unit 3 consists of a cylinder 4 known per se with a smooth bore 47 having a constant inside diameter d _3. The end 21 of the cylinder 4 contains a tab 54 provided with a bore 56 for fastening a to the tower ring 6 (FIG 1) arranged bearing 5. The other end 22 of the cylinder 4 contains a sealing element 57 and a guide bushing 58 for guiding and sealing the piston rod 7. At the outer end of the piston rod 7 there is a fork piece 59 for attachment to the bearing 50 of the base piece 13 (FIG 1) provided.

The end of the piston rod 7 located within the cylinder 4 is designed as a differential piston 14 equipped and slidable on the wall of the bore 47 with low-friction sealing and guide elements 60. The differential piston 14 contains a hydraulically unlockable 2/2-way valve 17 with two connections and two specific switching positions. In Fig. 2, the Wegevehtil 17 is shown in the closed position, so that the cylinder chamber 15 surrounding the piston rod 7 is not connected via the inlet 18 and outlet opening 19 of the differential piston 14 directly to the cylinder chamber 16 delimited on one side by the differential piston 14. The cylinder chamber 15 has a connection 23 at the end 22 and the cylinder chamber 16 has a connection 24 to the control unit 2 at the end 21. Within the control unit 2, these connections 23, 24 can be connected indirectly via hydraulic lines 34, 35, 36 and via a between the lines 35 , 36 located adjustable throttle valve 20 are connected to each other. However, the throttle valve 20 is also closed, so that in the arrangement according to FIG. 2 there is also no external connection of the cylinder spaces 15, 16.

To set the control functions «stop (Fig. 2),« slow forward (Fig. 3) and «fast forward» (Fig. 4) is within the Control unit 2 a known 4/3-way valve arranged as a switching valve 26, the switch 61 outside of the control unit 2 can be operated manually. In addition, the control unit 2 contains a further 4/2-way valve 27, which can only assume a second switching position 29 automatically as a function of pressure compared to a first basic switching position 28 in the fast forward switching position (FIG. 4) via a connecting line 45. Both valves 26, 27 are each connected to a pressure line 31 and a drain line 37, which can be connected outside the control unit 2 via the quick-action couplings 30 to the respective supply network of the barrel weapon.

The switching valve 26 is connected to the cylinder chamber 16 via the lines 62 and 36. In the wiring harness of line 62 there is an unlockable check valve 40 connected to the switching valve 26 with a pilot control line 42.

The directional control valve 27 in the basic position 28 connects to the lines 34 and 35 via a line 33 and a check valve 38 which is open in the inflow direction 64 (FIG. 3). Between the directional valve 27 and the check valve 38, the control line 32 of the unlockable directional valve 17 is connected to the line 33, which is connected to the front end of the piston rod 7 and continues within the piston rod to the directional valve 17. Another controllable throttle valve 46 is located in the connecting line 65 between the pressure line 31 and the 4/2-way valve 27.

In the switching position 44 "stop of the switching valve 26, the connection of the pressure line 31 to the cylinder chamber 16 is interrupted and the check valve 40 is closed, so that when the check valve 38 is also closed and the hydraulically controlled directional valve 17 and the manually closed throttle valve 20, the piston rod 7 does not move through in the direction 12 pulling force of the pipe recoiler in direction 10 (Fig.4) or through the differential piston 14 in direction 9 (Fig. 3) is movable.

3, the pressure line 31 is connected to the pilot line 42 of the check valve 40, whereby the check valve 40 is unlocked and the hydraulic medium 25 with the throttle valve 20 closed from the cylinder space 16 in the outflow direction 63 via the Line 62 can be pushed out into the drain line 37. The pressure line 31 is in the basic switching position 28 of the directional control valve 27 directly connected to the cylinder chamber 15, into which the hydraulic medium 25 can flow in the inflow direction 64, the piston rod 7 against the force of the pipe recoiler pointing in the direction 12 in the direction 9 and by the controllable Throttle valve 46 is retractable with different return speeds.

4, the pressure line 31 is connected to the cylinder space 16 via the automatically opened check valve 40. As a result, the directional control valve 27 is able to assume the second switching position 29 in a pressure-controlled manner via the line 45. In this switch position 29, however, the connection of the pressure line 31 to the line 33 is interrupted and the line 33 is connected to the drain line 37, so that the control line 32 is relieved of pressure and the directional control valve 17 when the check valve 38 and the throttle valve 20 are closed, which is under the force of Pipe recuperator in the cylinder space 15 building pressure is open and the hydraulic medium 25 in the case of the differential piston 14 which can be moved forward in the direction 10 directly, quickly and without any appreciable hydraulic resistance through the openings 18, 19 and through the relatively large nominal size of the directional control valve 17 from the cylinder space 15 in can flow the cylinder chamber 16. Due to the different diameters d, the piston rod 7 and d _{2 of} the differential piston 14, in addition to the amount of liquid flowing in from the cylinder space 15, the remaining amount required for fast forward flow in the inflow direction 64 through the lines 31, 62 and 36 into the cylinder space 16.

5, the speed simulator 1 can also be used to set variable slow forward speeds of the piston rod loaded in the direction of force 12 by the tube recuperator and thus of the parts 8 leading in the direction 10 (FIG. 1).

In the switching position 44 "stop" of the switching valve 26 and in the basic switching position 28 of the directional control valve 27 and when the directional control valve 17 is closed, the hydraulic medium 25 can flow out of the cylinder space 15 with the throttle valve 20 open differently and via lines 31, 33, 35 and 36 in the direction 64 flowing hydraulic medium 25 flow differently throttled into the cylinder space 16 in accordance with the desired forward speed.

In addition to the use case described and advantageously suitable in a narrow pipe return space 41 (FIG. 1) of a Pahzer howitzer, the speed simulator 1 (FIG. 1) is particularly low in energy consumption and with a high hydraulically transferable return force of, for example, 80 kN, due to its small, preferably nominal size 6 mm dimensioned connecting lines and valves can still be carried manually, so that the speed simulator 1 can also be used for the repair work of other large-caliber barrel weapons, not shown, with caliber diameters s: 90 mm and relatively high recoil forces, for example in the field.

Reference symbol list

• 1 speed simulator
• 2 control unit
• 3 piston-cylinder unit
• 4 cylinders
• 5 bearings
• 6 tower ring
• 7 piston rod
• 8 part
• 9 direction
• 10 direction
• 11 gun barrel
• 12 direction
• 13 bottom piece
• 14 differential pistons
• 15 cylinder space
• 16 cylinder space
• 17 way valve
• 18 inlet opening
• 19 outlet opening
• 20 throttle valve
• 21 end
• 22 end
• 23 connection
• 24 connection
• 25 hydraulic medium
• 26 switching valve
• 27 way valve
• 28 basic switching position
• 29 switch position
• 30 quick release coupling
• 31 pressure line
• 32 control line
• 33 line
• 34 line
• 35 line
• 36 line
• 37 drain pipe
• 38 check valve
• 39 switching position
• 40 check valve
• 41 room
• 42 pilot line
• 43 switch position
• 44 switch position
• 45 connecting line
• 46 throttle valve
• 47 hole
• 48 tower
• 49 bolts
• 50 bearings
• 51 cradle tube
• 52 trunnion axis
• 53 Index position
• 54 tab
• 55 weapon barrel axis
• 56 hole
• 57 sealing element
• 58 guide bush
• 59 fork piece
• 60 sealing and guiding element
• 61 switches
• 62 management
• 63 Outflow direction
• 64 Inflow direction
• 65 connecting line
  • d, diameter
  • d ₂ diameter
  • d ₃ inner diameter
• h piston stroke
  • 1 ₁ Gun barrel return length
  • 1 ₂ distance
  • 1 ₃ installation length

Claims (9)

1. Velocity simulator (1) for monitoring the parts (8) of a large-calibre weapon barrel (11) which recoil and advance in the process of firing, with a control and piston cylinder unit (2, 3) interconnected on the block assembly system and of which the piston rod (7) belonging to a differential piston (14) and extending from one side of the cylinder moves back the recoiling and advancing parts (8) in opposition to the force of a barrel recuperator, characterised by the following features :

a) within the control unit (2) hydraulic control valves (20, 26, 27) are provided which, together with a further valve (17) positioned inside the differential piston (14) allow the monitoring of movements of a variable velocity recoil and advance action and also of a rapid advance corresponding to the maximum forward movement velocity and ensure any desired secured interruption.

b) the block of the velocity simulator (1) formed from the control unit (2) and the piston cylinder unit (3) has a sufficiently short installation length (13) to enable it to be manually fitted into a narrowly dimensioned installation compartment (41) with a weapon barrel (11) which has recoiled by the barrel recoil length (11) with a residual distance (12) left between a base piece (13) and a turret rim (6) and shorter than two barrel recoil lengths (11) on the weapon barrel axis (55) prolonged beyond the base piece (13).

2. Velocity simulator in accordance with Claim 1, characterised by the following features :

a) within the cylinder (4) for the movement of the piston rod (7) the cylinder chamber (15) can be subjected to hydraulic medium via a connection 23) and the cylinder chamber (16) delimited by the differential piston (14) can be subjected thereto via a connection 24 separately from the control unit (2),

b) the valve (17) of the differential piston (14) is a releasable 2/2 -way valve, so that for the simulation of the rapid unbraked advance movement the hydraulic medium (25) can flow direct from the cylinder chamber (15) into the cylinder chamber (16).

3. Velocity simulator in accordance with Claim 1 or 2, characterised by the fact that within the control unit (2) a known type of 4/3 way valve is provided as an operable control valve (26) through which the control functions slow recoil (Figure 3), rapid forward « movement (Figure 4) and « stop (Figure 2) are variably adjustable.

4. Velocity simulator in accordance with one of Claims 1 to 3, characterised by the fact that within the control unit (2) an adjustable throttle valve (20) is provided which is controllably connected with the connections (23, 24) of the cylinder chamber (15, 16) in such a manner that the hydraulic medium (25) can flow at a different speed from the cylinder chamber (15) into the cylinder chamber (16) and only the forward movement (Figure 5) of the piston rod (7) in the direction (10) is adjustable to varying speeds.

5. Velocity simulator in accordance with one of Claims 1 to 4, characterised by the following features :

a) within the control unit (2) a known type of 4/2 -way valve (27) is provided which, when the control valve (26) occupies the control position « rapid forward movement », via a connection line (45) it automatically assumes, in accordance with the pressure, a second control position (29) as opposed to a first basic control position (28),

b) in the first basic control position (28) a pressure pipe (31), connectable via a rapid-closure coupling (30) to a hydraulic energy supply system, is directly connected, for the rapid recoil of the piston rod (7), via pipes (34) to the connection (23) of the cylinder (15) or, for slow forward movement of the piston rod (7), with the throttle valve (20) open, via pipes (33, 35, 37) to the connection (24) of the cylinder chamber (16) while for locking the directional control valve (17), between the directional control valve (27) and the connection (23) a control pipe (32) is connected to the pipe (33),

c) in the second control position (29) the pressure pipe (31) is interrupted, the control pipe (32) relieved of pressure and connected to a discharge pipe (37) connectable to a tank, whereas the pipes (34, 35) are shut off from the pipe (33) by a non-return valve (38).

6. Velocity simulator in accordance with one of Claims 1 to 5, characterised by the fact that when the control valve (26) occupies the control position (39); « slow recoil the pressure pipe (31) is connected with the preliminary control pipe (42) of a releasable non-return valve (40) of a type known per se, and situated between the control valve (26) and the cylinder chamber (16) and the non-return valve (40) is open, so that, to enable the hydraulic medium to flow out, the cylinder chamber (16) is connected to the discharge pipe (37) via the control valve (26).

7. Velocity simulator in accordance with one of Claims 1 to 6, characterised by the fact that when the control valve (26) occupies the control position (43), « rapid forward movement", the pressure line (31) is connected to the cylinder chamber (16) via the automatically opened non-return valve (40) so that by reason of the different diameters (d1) of the piston rod (7) and (d2) of the differential piston (14), the residual quantity of liquid required for rapid forward movement can flow into the cylinder chamber (16) in addition to the quantity flowing in out of the cylinder chamber (15).

8. Velocity simulator in accordance with one of Claims 1 to 7, characterised by the fact that when the control valve (26) occupies the control position (44) « stop •, the connection of the pressure pipe (31) with the cylinder chamber (16) is interrupted and the non-return valve (40) is closed, so that when the non-return valve (38), the directional control valve (17) and the throttle valve (20) are closed the piston rod (7) is not movable in the directions (9, 10).

9. Velocity simulator in accordance with one of Claims 1 to 8, characterised by the fact that the pressure pipe (31) is connected to the 4/2-way valve (27) via an adjustable throttle valve (46) so that the recoil speed of the piston rod (7) in the direction (9) is adjustable.

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