JPH0560493A - Drive mechanism having built-in gatling type gun - Google Patents

Abstract

PURPOSE: To obtain a hydraulic driving device which takes out energy from the rotation of a gun tube bundle around the axis of a Gatling gun, by mechanically coupling a mechanical driving device containing a pressure accumulator to the gun tube bundle and giving initial acceleration, rotating speed control, braking, and residual bullet removing reverse operation to the gun tube bundle by driving the driving device by means of the gun tube bundle and driving the gun tube bundle by means of the driving device. CONSTITUTION: A variable displacement over-center piston pump/motor 100 having the servo valve 102 of a hydraulic driving device 15 is mechanically coupled with the rotor 136 of a Gatling gun containing a gun tube bundle. A pressure accumulator 104 has a charging valve assembly 105, makes initial-pressure charging of a gas isolated from a hydraulic fluid by means of a piston or function, and is connected to the discharge port 100a of the pump/motor 100 through a check valve 106, a flow control valve 108 connected in series with the valve 106, and a high-pressure connecting section 109. The pressure from the pressure accumulator 104 is supplied to the motor mode input port 100a of the pump/motor 100 and starts and accelerates the rotor 136 of the Gatling gun in the advancing/firing rotational direction through a gear box 134.

Description

Description: TECHNICAL FIELD The present invention relates to a Gatling type gun device which has a built-in power source and can be started by itself.

 (Prior Art) An automatic gun device that requires external power was about one digit more reliable than a conventional self-contained gun device.

In large caliber machine guns, the conventional built-in power was a direct drive unit that was operated by the retreat or gas of the gun, but conventionally, an electric motor, pneumatic drive or hydraulic drive was used as external power. This was true even in the Gatling type gun, which is a continuous motion device that has been inherently more reliable than the single-arm gun that is a reciprocating device.

 H.M. Otto announced in US Pat. No. 2,849,921 issued September 2, 1958, a new type of Gutling gun driven by an external electric motor.

 RR Bernard et al. Are driven by internal gas pistons in US Pat. No. 3,311,022 issued March 28, 1967, and RE Chaiabrandy in US Pat. No. 3,407,701 issued October 29, 1968. The new Gutling gun has been announced.

 E. Ashley et al. In U.S. Pat. No. 3,535,979 issued Oct. 27, 1979, disclosed an automatic percussion spring starter and brake for a Gutling mechanism.

 L.R. Folsom et al. In U.S. Pat. No. 3,568,563, issued on March 9, 1971, introduced a Gutling gun of the type that presses a spring that drives the gun by an internal gun gas vane motor.

 D.A. Farrington in U.S. Pat. No. 3,703,122, issued Nov. 21, 1972, introduced a muzzle torque increasing device for Gattling guns.

 N.C. Garland et al. In U.S. Pat. No. 3,991,650, issued November 16, 1976, have disclosed a hydraulic system that extracts energy from the rearward movement of a gun to start and drive a Gutling gun.

 G.W Carrie, in US Pat. No. 4,046,056 issued Sep. 6, 1977, announced an air system that extracts energy from a pressurized tanker to start and drive a Gutling gun.

 An electrohydraulic drive that is constantly powered by the aircraft hydraulics was announced in the US Air Force T.O.11W1-28-8-2, published July 1, 1976.

(Problems to be Solved by the Invention) There is a limit to the power of the device for starting and driving the gun with the energy that can be extracted from the backward movement of the housing of the Gutling type gun, and therefore the firing speed of the gun is limited. It turns out that there is a limit.

 However, in a Gutling gun, the rotation of the cluster of gun barrels with the muzzle torque augmentation device provides adequate surplus energy to recharge the hydraulics that start and drive the gun. It is possible.

 An object of the present invention is to provide a hydraulic drive system for driving a Gatling type gun that extracts energy from rotation of the barrel bundle about the gun axis.

 It is another object of the present invention to provide a hydraulic drive system for starting, driving, controlling speed, and performing reverse maneuver removal of a Gutling gun.

(Means for Solving the Problems) A feature of the present invention is to provide a gun apparatus including a Gutling type gun, in which a barrel bundle has a torque increasing device and is connected to a hydraulic drive device, The object is to provide a gun device that performs initial acceleration of the gun, rotation speed control, braking and reverse operation depletion, and a gun gas drive mechanism that supplies steady state energy for rotation of the barrel bundle.

(Embodiment) FIG. 1 shows a gun device 10 according to an embodiment of the present invention.

The construction includes, for example, a Gutling gun of the type shown in U.S. Pat. No. 4,342,253 issued August 3, 1982 by RG Kirk-patrick et al., And, for example, J. Dix (Dix). ), Et al., Including an ammunition handling device of the type shown in U.S. Pat. No. 4,004,490 issued January 25, 1977.

 The gun system 10 has two main drive elements, one on the gun gas drive mechanism 16 (shown in FIG. 2) and on the rotary barrel 14 for producing steady state energy. The torque increasing device 13 is the other, and the other is a hydraulic drive device 15 for performing initial acceleration, speed control, braking, and reverse operation residual ammunition removal. The gun gas drive mechanism 16 and the torque increasing device 13 can generate more energy than is necessary for the gun at a desired rate of fire. This excess energy is used to recharge the hydraulic drive 15 which includes a high pressure hydraulic source connected to a hydraulic motor used to provide the initial acceleration or starting function of the gun. This hydraulic drive 15 is also used for reverse debris removal, rotational speed control and dynamic gun braking. After the initial filling, the hydraulic drive unit 15 requires no external power except for control signals (for example, start, stop, etc.) from the electric control unit. This hydraulic drive can eliminate the need for conventional heavy and bulky drives and associated power supplies on aircraft and rotary turrets.

 The graph of FIG. 8 shows that energy is available to fill the storage device. The power output of the piston drive is a direct function of the gun's rotational speed. The power output of the muzzle torque augmentation device is a function of the square of the gun's rotational speed. The rate of rotation of the gun is a direct function of the rate of fire of the gun. The difference between the rotational speed of 2000 rounds per minute that the gun becomes constrained and the virtual speed of 2400 rounds per minute or more when unconstrained is the product of the rotational speed and the deterrent torque. Energy is available for storage.

 As shown in FIGS. 2, 3 and 4, the gun gas drive mechanism 16 includes a piston 20, a head 22 of the piston 20 is placed in a cylinder 24, and a rod 26 of the piston 20 The front end is pivotally attached to the head 22, and the rear end of the rod 26 is pivotally attached to the crank 28. The ring gear 30 is fixed to the housing 9 by the foundation 32 and does not rotate. The foundation 32 can be adjustable so that the ring gear 30 and the crank 28 can be synchronized. The inner ring 34 has a plurality of arms 36 fixed to the cylinder 24 and forming a spider. The cylinder 24 is secured to the barrel bundle 14 by means of a clamp plate 40. Crank 28 has a pair of distally extending shafts 42, each fitted with a spider, one of which has a pinion gear fixedly engaged with ring gear 30. Thus, as the piston 20 reciprocates, the crank 28 rotates, driving its pinion gear with the cylinder 24 and barrel bundle 14 in an orbit around the ring gear. As shown in FIG. 3, the gas outlet port 46 of each barrel 47 is aligned with its respective gas inlet port at the front end of the cylinder 24, with the bullets 50 along the bore 49 of each barrel 47. A part of the gun gas to be propelled can be guided to the chamber 51 formed at the front end of the cylinder 24 to drive the piston head 22 backward. When the piston head reaches the end of its backward movement, it opens the gas exhaust port 52 leading to the exhaust manifold 54 in the wall of the cylinder 24 and thus to the exhaust pipe 56, as shown in FIG.

The piston 20 performs a complete reciprocating cycle with each firing of each barrel. Therefore, if there are five barrels, each rotation of the barrel bundle 14 will cause five cycles of piston reciprocation. The gas port connecting the cylinder 24 and the barrel that does not ignite remains open during the power stroke of the piston, but the movement of the piston is rapid and its area is much larger than that of the gas port. Most of the work done by is distributed to the piston without leaking. Also, the amount of energy obtained from the gas is so large that efficiency is not the first consideration.

 Both the ring gear and the pinion gear may be conventional bevel gears or spur gears and surface gears.

 The torque increasing device 13 may be of the type shown, for example, in U.S. Patent Application No. 617,052 filed June 1, 1984 by C.E. Hillman. The torque-increasing device includes multiple radial flow turbines, each centered on the corresponding barrel. Each turbine bends a portion of the gun's gas in a semi-radial direction, producing pure torques centered on each barrel, and without any lateral loading on the stationary part of the gun, Concentrate on torque with the vertical axis as the center.

 A first embodiment of the hydraulic drive 15, ie the hydraulic starting part, is shown in FIGS. 5, 6 and 7. A variable displacement overcenter piston pump / motor 100 having a servo valve 102 for controlling the yaw angular position is mechanically coupled to a gun rotor 136 including a barrel bundle 14 via a gearbox 134. ..

The Pump / Motor 100 is an axial piston motor, several of which are extended by high-pressure fluid, as laid out on page 159 of Machine Design, September 29, 1983. It typically includes a cylinder with 7-9 pistons. One end of these pistons is constrained by an angled plate supported by a yoke. As these sequentially receive the force that supports the plate, a rotational force is generated to rotate the piston.

In many designs, the shaft is driven directly by either a cylinder or a cam plate, and in a few hydraulic motors the shaft is driven using a differential gear that allows low speed and high torque. As a pump, the yoke is overcenter-shifted so that its angular position is reversed, and the shaft drives the piston.

 The accumulator 104 has a fill valve assembly 105 for initial pressure filling of the gas separated from the hydraulic oil by a piston or bladder, and through a check valve 106 and a flow limiting valve 108 in series therewith a high pressure connection. Connected via pump 109 to pump / motor 100 exhaust port 100a. The check valve 106 and the flow rate limiting valve 108 are arranged in parallel with the solenoid valve actuated on / off valve 110 and check valve 112. The pump mode suction port 100b of the pump / motor 100 is connected to the low pressure connection 113. The hand pump 114 and the check valve 116 are connected in series between the pressure accumulator 104 and the low pressure connection portion 113. A manual bypass valve 118 is connected between the high pressure connection 109 and the low pressure connection 113. A solenoid operated on / off valve 120 connects the servo actuator controller 102 and the pressure accumulator 104. The device safety valve 122 is connected to the high pressure connection 109 and one low pressure port 124a of the bootstrap reservoir 124, and the other low pressure port 124b is connected to the low pressure connection 113. A filter 123 may be connected between the case drain 100C of the motor 100 and the port 124a of the liquid storage tank 124.

 In order to accelerate the gun rotor 136 to firing speed, the servo on / off valve 120 must open and the servo actuator control valve 102 must act to switch the pump / motor overcenter valve plate from pump mode to motor mode. In addition, the solenoid operated on / off valve 110 must be opened to connect the accumulator to the high pressure connection 109 via the high pressure connection 109. The pressure from the accumulator 104 is supplied to the motor mode inlet port 100a to start and accelerate the gun rotor 136 in the forward / fire rotation direction via the gearbox 134. At maximum rate of fire, the solenoid operated on / off valve 110 must be closed.

 At normal gun load torque, pump 100 is suitable for full displacement because it limits the rotational speed of gun rotor 136 when the pressure in accumulator 104 is low. During firing, the pressure accumulator 104 is refilled by the pump 100 via the flow rate limiting valve 108 and the check valve 106, and the pressure filling of the pressure accumulator 104 is raised to normal or higher. As the pressure in the accumulator 104 increases, the servo controller 102 reduces the displacement of the pump so that the full load torque of the device at its firing rate is commensurate with the full output of the device, including the muzzle torque booster. Control the rotation speed of. If the rotation speed of the barrel bundle changes, the servo controller adjusts the displacement of the pump 100 and the pump load to maintain or restore the firing speed.

 When the gun load torque falls below the normal level, the pump with full displacement reaches the set value of the flow rate limiting valve 108 at the rotation speed of the barrel bundle at the standard value, and the flow rate limiting valve supplies the necessary back pressure to store the accumulator 104. Suppress the rotation speed of the barrel until it is filled to the required high back pressure.

 In the case of continuous firing over the normal pressure, the pressure accumulator 104 is filled with the normal pressure or higher. The device safety valve 122 opens during each firing to limit the maximum fill pressure to the accumulator 104 by diverting fluid to the low pressure connection 113 through ports 124a and 124b of the bootstrap reservoir 124. Is set as follows.

 When the gun's gunbolt firing needle had a safety device and hitting the ammunition stopped, no more gun gas was produced, the gun gas drive was de-energized, the gun torque load and the pump braking the barrel bundle. To stop this. The check valve 106 prevents the pump 100 from rotating in the reverse direction as a motor. The solenoid on-off valve 110 will work if it is completely stopped and will press the motor mode suction port 100a via the high pressure connection 109 to cause the pump / motor to act as a motor in the reverse debris removal direction-i.e. Rotate the gun barrel in a direction that does not fire it. When the debris removal is completed, the valve 110 stops its operation, and the high pressure is removed from the connection portion 100a to stop the function of the reverse motor.

 As can be seen in FIGS. 6 and 7, the hydraulic servo pump / motor 100 and the gearbox 134 are pump / grooved on the cylinder block or sleeve 202 and also on the coupling shaft 204. A housing 198 with a motor shaft is included, the coupling shaft is grooved to the input shaft / gear 208, which meshes with the output shaft / gear 208, which in turn is grooved to the gearbox input shaft / gear 212. The gearbox input shaft / gear 212 is further meshed with the input gear 214 of the differential gear assembly 216, and the output gear 218 of the differential gear assembly is finally inserted into the output coupling shaft 210. It engages with the ring gear 30 of the rotor 136 of the turret to drive the barrel bundle, feeder and ammo handling equipment.

 The yoke 220 has two sets of integrated coaxial stub shafts 222, each pivotally fitted into a roller bearing 224 about an axis 226 perpendicular to the axis of rotation 228 of the axis 200. An annular wear plate 230 is secured to it and pivoted to the yoke 220. Cylindrical block 202, which is slotted into shaft 200 and rotates with it, has a plurality of cylinders 232 arranged in an annular row concentric with shaft 228. Each cylinder 232 has a respective piston 234 with an integral piston rod 236, which piston 234 terminates in a ball 238. The ball 234 carries a shoe 240, which rests on a wear plate 230. Each cylinder 232 has a port 242 which sequentially aligns with the high pressure port 244 and low pressure port 246 on the stationary valve plate 248 each time the block 202 makes one revolution of the shaft 228.

The high pressure port 244 is connected to the high pressure connection 109 via a manifold 250. The low pressure port 246 is connected to the low pressure connection 113 via the manifold 252.

 The magnetic sensor 254 is fixed adjacent to the input gear and the teeth of the shaft 206 and produces an output signal used to determine the rotational speed of the shaft 200.

 The tilt of the yoke 220 is controlled by two piston assemblies 260 and 260 '. Each piston assembly is fixed to the housing 198 and consists of a cylinder 264, a port 266 and a respective piston sleeve having a piston 268. Each piston has a piston rod 270, each having an upper knuckle 272 grasped by a piston 268 and a lower knuckle 276 grasped by a socket 278 in the yoke. Yoke stops 280 are each fixed to the housing opposite the piston and limit movement within the piston extension. One port 266 is connected to the high pressure manifold 250 via a conduit. The other port 266 'is connected via a conduit to the servo control manifold.

 FIG. 9 shows the hydraulic drive system in the second embodiment in the stop position. The housing 300 includes a high pressure manifold 302 connected to a high pressure accumulator 304 and a low pressure manifold 306 connected to a low pressure accumulator 307. These accumulators are connected by a hydraulic drive to an axial piston motor 308, which can be reversed depending on which of its main ports is connected to the high pressure side, and its displacement is progressively maximized. And can be changed to a minimum. The accumulator air pressure can be supplied from another refillable high pressure vessel not shown.

 In the rest position, the high pressure of the high pressure manifold 302 is supplied to both sides of the suction port 310 of the forward solenoid valve 312, the suction port 314 of the reverse solenoid valve 316, and the control piston 318. Due to the equal high pressure on both sides, the control piston 318 is in equilibrium and the spring 320 can push the motor control spool 322 against the stop 324 and bias it to the right closed (stop) position. The action of notch 334 connects motor inlet port 336 with low pressure chamber 238 via manifold 335. The motor exhaust port 342 is also tied to the low pressure section via the manifold 337 so that the motor does not start in the stop position.

 When the trigger signal is applied, the forward solenoid valve 312 is activated and the high pressure is removed from the left side of the control piston 318. The high pressure on the right side of the control piston 318 pushes the piston to the left, compressing the spring 320. This allows the spring 338 to move the motor control spool 322 to the left, leading high pressure through the chamber 309 from the manifold 302 to the manifold 335, activating the motor 308 and accelerating the gun to full speed. During this acceleration, the gun gas drive 16 assists the motor to raise the gun to full speed as the firing occurs. When the motor and gun reach about 90% of full speed, a speed sensor, not shown, sends a signal to an electronic controller, also not shown, which simultaneously turns off the forward solenoid valve 312 and turns on the reverse solenoid valve 316. Both valves now act to apply high pressure to the left side of control piston 318, releasing high pressure on the right side. The forces of spring 320 and control piston 318 combine to move motor control spool 322 to the right, past the normally closed (stop) position to the reverse position and compress springs 238 and 239. The stop 324, which determines the stop position of the motor control spool 322, is held to the left by the force of the spring 339. Here, the inlet 336 to the motor is connected to the low pressure accumulator 307 via the chamber 340, the central cavity 330 of the motor control spool, and the notch 334. The discharge port 342 of the motor is connected to the high pressure accumulator 304 through the check valve 354 because the discharge passage to the normal low pressure accumulator is closed here. This condition is maintained during steady-state gun fire when the gun gas drive mechanism powers the gun equipment and also drives the motor 308 which acts as a pump to fill the high pressure accumulator 304 through the check valve 354. It When the pressure of the high pressure accumulator reaches a specified limit value, the front safety valve 350 opens and the fluid pumped from the motor outlet 342 is recirculated to the motor inlet 336.

 In order to maintain steady state speed control in the forward direction, the displacement of motor 308 must be variable in order to produce a constant load torque as was required in hydraulic drive example 1. If the pressure in the high pressure accumulator rises as the accumulator is charged by the motor, the displacement of the motor must be small to keep its load torque constant. The displacement control servo 308a performs this function.

 After the trigger signal is released and the last bullet fired, the gas drive mechanism 16 stops supplying power to the gun device, and the inertia of the gun device's rotation causes the motor 308 to continue to load as a pump, causing a rapid decrease. Be speeded up. During this time, the motor control spool 322 may cause the gun device to fill the high pressure accumulator 304, depending on the length of the rate of fire, or it may cause the fluid from the motor outlet 342 to enter the motor inlet as described above. Control either to recirculate to 336.

 When the motor speed is zero, the high pressure from the accumulator 304 flows through the motor control spool, through the notch 326, the check valve 352, and the flow restrictor 353 to the motor outlet 342, which causes the motor to run in the opposite direction. Accelerate to.

The reverse rotation speed of the motor is controlled by setting the flow rate limiter 353.

 The controller deactivates the reverse solenoid valve after pulling back the unfired bullet from the gun. When the reverse solenoid valve deactivates, high pressure is applied to the right side of the control piston 318, and the force of the spring 338 and spring 339 is applied to move the motor control spool 322 to the left. When the motor control spool moves to the left, the force of spring 339 also acts on stop 324, moving it in the same direction to the end of travel, the stop position. When the stop 324 is in the stop position, the spring 339 cannot move the motor control spool 332 any further to the left, and the motor control spool is moved to the stop 324 by the force of the spring 320 which exceeds the opposing force of the spring 338. It stops at the closed (stop) position. When the pressure reaches the set value of the check valve, the check valve opens. With the reverse safety valve open, hydraulic fluid flows from the motor inlet 336 to the motor outlet 342. The hydraulic fluid thus continues to circulate until the motor is stationary.

[Brief description of drawings]

 FIG. 1 is a perspective view of a gun device according to an embodiment of the present invention. FIG. 2 is a perspective view of a gun gas drive mechanism that provides steady state energy for rotation of the barrel of the gun. FIG. 3 is a detailed view showing the work stroke of the gun gas drive mechanism of FIG. FIG. 4 is a detailed view showing the exhaust stroke of the gun gas drive mechanism of FIG. FIG. 5 is a system diagram of the first embodiment of the hydraulic drive system. FIG. 6 is a vertical sectional view of a hydraulic servo pump / motor of the hydraulic drive system of FIG. FIG. 7 is a vertical cross-sectional view of a detail rotated by 90 ° with respect to FIG. 6. FIG. 8 is a graphical representation of the energy available as power for the hydraulic drive system of FIG. FIG. 9 is a system diagram of a second embodiment of the hydraulic drive system. 9 ... Housing, 10 ... Gun device, 13 ... Torque increasing device, 14 ... Gun bundle, 15 ... Hydraulic drive device, 16 ... Gun gas drive mechanism, 20 ... Piston, 22 ... Piston head, 24 ... Cylinder, 26 ... Rod, 28 ... Crank, 30 ... Ring gear, 36 ... Arm, 44 ... Pinion gear, 46 ... Gas exhaust port, 47 ... Barrel, 49 ... Gun cavity, 50 ... Bullet, 51 ... Chamber, 52 ... Gas exhaust port, 54 ... Exhaust manifold , 56 ... Exhaust pipe 100,308 ... Pump / motor, 106,112,354 ... Check valve, 104 ... Accumulator, 105 ... Valve assembly, 109 ... High pressure connection, 113 ... Low pressure connection, 114 ... Hand pump, 118 ... Bypass valve, 123 ... Filter, 124 ... Reservoir, 134 ... Gear box, 136 ... Rotor, 198,300 ... Housing, 214 ... Input gear, 216 ... Differential gear assembly, 218 ... Output gear, 220 ... Yoke, 254 ... Magnetic sensor, 318 ... Control piston, 332 ... Control spool, 342 ... Over data outlet

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁵ Identification code Office reference number FI technical display location F41C 3/14 7040-2C

Claims (5)

[Claims] 1. A Gutling gun device, comprising: a housing; a barrel bundle rotatably supported with respect to the housing; a barrel bundle coupled between the housing and the barrel for receiving gas from the barrel barrel; Is a hydraulic drive including a gun gas drive mechanism for rotating the gun with respect to the housing, and a pressure accumulator, which is mechanically coupled to the barrel bundle, is driven by the barrel bundle, and drives the barrel bundle. And a hydraulic drive device for imparting initial acceleration, rotation speed control, braking, and reverse operation detonation to the bundle of gun barrels. 2. The gun device according to claim 1, wherein the hydraulic drive device includes a hydraulic motor, the hydraulic motor being hydraulically coupled to the accumulator and mechanically coupled to the barrel bundle. When the gun barrel is driven by a gun gas driving device, a hydraulic motor is driven by the gun barrel to pressurize a pressure accumulator. 3. The gun device according to claim 1, wherein the hydraulic drive device includes a hydraulic motor, the hydraulic motor being hydraulically coupled to the accumulator and mechanically coupled to the barrel bundle. The gun equipment is characterized in that the hydraulic motor is driven by the pressure from the accumulator to start the rotation of the barrel bundle in the firing rotation direction to start the operation of the gun gas drive mechanism. 4. The gun device according to claim 1, wherein the hydraulic drive device includes a hydraulic motor, the hydraulic motor being hydraulically coupled to the accumulator and mechanically coupled to the barrel bundle. A gun device characterized in that a hydraulic motor is driven by pressure from a pressure accumulator to rotate a barrel bundle in a direction opposite to a firing rotation direction. 5. The gun device according to claim 1, wherein the barrel bundle has a torque increasing device at the muzzle end of the barrel, and the gun gas present in the barrel cavity rotates the barrel bundle relative to the housing. A gun device characterized by bending a flow to give rotational energy.