Hydraulic torsion straight spin pop-up bumper

Abstract

The hydraulic torque straight-rotation spring buffer disclosed by the application has reliable spring buffering and stable buffering effect. The technical scheme is as follows: a damping adjuster corresponding to a stop bushing is arranged in the middle of an outer cylinder, left and right rotating torsion springs for providing torsion moments are arranged on the outer cylinder and constrained on a torsion spring pressing block and located on both sides of the damping adjuster; the damping adjuster forms damping force through a damping hole of a built-in damping element; the straight-rotation pistons slide back and forth along the oil cylinder wall in the direction of two damping cavities separated by the stop bushing, thereby generating resistance movement; meanwhile, the damping oil in the damping cavities is compressed, double oil paths enter two side oil supplement cavities, and the hydraulic damping is relied on to buffer the mechanical switch device, the two straight-rotation pistons rotate to a fixed angle, the internal structure provides a torsion damping moment to the left and right rotating torsion springs, the left and right rotating torsion springs pressed by the torsion spring pressing block on the bolt are buffered and relaxed under the action of the torsion moment, and the buffered switch device is opened.

Description

Technical Field

[0001] This invention relates to the field of energy absorption technology, specifically a hydraulic buffer mainly used in engineering machinery, transportation vehicles, and light industrial and textile machinery, particularly suitable for the direct-rotation spring-loaded buffer of deceleration parachute doors. Background Technology

[0002] With the rapid development of large-scale, automated, and high-speed machinery using buffers in modern production, the chances of collision accidents due to various operational errors have increased, and the intensity and destructiveness of collisions have greatly increased. Therefore, the performance requirements for buffers are becoming increasingly stringent. Buffers are generally cylindrical structures, mainly composed of pressure-bearing components, buffering components (medium), reset components, and a housing. The function of a buffer is to absorb the impact force generated during equipment operation, thereby effectively protecting and mitigating equipment damage caused by collisions. The state has strict regulations and restrictions on the manufacture and use of buffers. The built-in torsion spring type hydraulic damping hinge used in civilian applications is one of the most common hydraulic hinges with door closer function on the market. A small hydraulic cylinder is built into the hinge's central shaft. A piston with a small return oil orifice slides back and forth along the cylinder wall, creating resistance—this is hydraulic pressure. When the hinge is opened, the torsion spring built into the hinge's central shaft twists and deforms, generating a reaction closing force. When the hinge is closed, the pressure generated by the torsion spring's twisting forces the hydraulic oil in the cylinder to flow through the small orifice of the piston. The small orifice diameter and slow oil flow rate hinder the torsion spring from closing quickly—this is damping. In civilian hydraulic hinges, the spring-loaded spring is arranged inside the damper, and the spring force provides the spring-loaded torque. Spring force utilization is relatively low, and multiple sets of hydraulic hinges are required. Hydraulic hinges provide spring-loaded torque and damping torque for a single output shaft, and generally two or more sets are used simultaneously. The use of hydraulic hinges is limited: the cavity is a mixture of oil and gas, and the damping cavity must be used vertically downwards. Due to the differences in materials and structural forms of various dampers, their application range and operating environments also differ. Hydraulic cylinder buffering methods can be divided into throttling buffering and pressure relief buffering. They can also be categorized by device type: one is an external buffer hydraulic cylinder. This involves using flow control devices such as relief valves, sequence valves, throttle valves, or accumulators within the hydraulic system for buffering. The advantage of external buffering is that the buffering elements are easily adjusted when operating conditions change. The disadvantage is a complex system circuit, and the buffering effect is easily affected by other parts of the system. The other is an internal buffer hydraulic cylinder. An internal buffer hydraulic cylinder generally utilizes the gap between a buffer plunger connected to the piston and a buffer hole connected to the cylinder body. When the oil flows through, resistance is generated, achieving the buffering purpose; hence, it is called throttling buffering. Throttling buffering utilizes the effect of throttling damping. When the buffer plunger is inserted into the drain hole, a closed space is formed between the piston and the hydraulic cylinder end cap. Oil in this closed space can only flow out from the throttling orifice or the throttling annular gap between the plunger and the drain hole, thus creating high pressure in the closed space, forcing the piston to decelerate and achieve buffering. During the buffering process, because the throttling area remains constant, this type of buffering device initially generates a large buffering braking force (significant effect), but it quickly decreases and eventually becomes ineffective, resulting in a poor and less than ideal buffering effect. However, this device is simple to manufacture and has low production costs, so it is often used in mass-produced hydraulic cylinders.

[0003] Hydraulic dampers are commonly used in lifting and transport machinery, metallurgical, port machinery, power, and railway transport vehicles. These machines operate at very high speeds, and malfunctions can cause significant damage. Therefore, hydraulic dampers are needed to slow down the movement of the machinery. Hydraulic dampers are energy-dissipating dampers, capable of absorbing 80% of impact energy. They have a large buffering capacity, balanced resistance, and no rebound during buffering. Hydraulic dampers are devices that slow down moving parts when they are close to their destination to prevent impact. The simplest buffering device is to change the oil circuit, sealing the original large orifice and allowing oil to flow out through a small orifice, thus reducing the flow rate and speed. Hydraulic dampers mainly utilize the incompressibility and fluidity of hydraulic fluid. By allowing the liquid to flow between a variable and a fixed cavity within a closed chamber, and leveraging the incompressibility of the liquid, the required pressure bearing capacity and buffering requirements are met. Hydraulic dampers typically utilize a series of specially designed throttling orifices on the cylinder wall for buffering. The number of throttling orifices decreases as the buffer displacement increases, thus achieving uniform speed buffering. They are used in cranes operating at speeds of 2 m / s or with large masses.

[0004] Hydraulic dampers are safety protection devices installed on track-running equipment. They consist of a pressure-controlled valve and a flow-controlled valve, forming a buffer system. The energy acting on the piston rod is converted into oil flow through the pressure control valve, thus achieving the buffering purpose. The hydraulic damper relies on hydraulic damping to buffer and decelerate the object acting upon it to a stop, and a built-in compression spring returns the piston rod to its initial position. It provides a certain degree of protection. Its function is to prevent damage to the mechanism caused by hard collisions during operation. Hydraulic cylinder buffering methods can be divided into throttling buffering and pressure relief buffering. From the perspective of device installation, there are two types: one is an external hydraulic damper. This involves using flow control devices such as relief valves, sequence valves, throttling valves, or accumulators in the hydraulic system for buffering. The advantage of external buffers is that the buffering elements can be easily adjusted when operating conditions change. The disadvantage is that the system circuit is complex, and the buffering effect is easily affected by other parts of the system. The other type is a built-in hydraulic damper. Built-in buffer hydraulic cylinders typically utilize the gap between a buffer plunger connected to the piston and a buffer hole connected to the cylinder body to generate resistance as oil flows through, achieving a buffering effect; hence, this is called throttling buffering. Throttling buffering utilizes the effect of throttling damping during operation. When the buffer plunger is inserted into the drain hole, a closed space is formed between the piston and the hydraulic cylinder end cover. Oil in this closed space can only flow out from the throttling orifice or the throttling annular gap between the plunger and the drain hole, thus creating high pressure in the closed space, forcing the piston to decelerate and brake, achieving buffering. During the buffering process, because its throttling area remains constant, the buffering braking force generated at the beginning is large (the effect is obvious), but it quickly decreases and eventually becomes ineffective, resulting in a poor buffering effect. However, this device is simple and has low manufacturing costs, so it is widely used in mass-produced hydraulic cylinders.

[0005] To shorten landing distance, aircraft employ wheel brakes. However, the deceleration effect of wheel brakes is limited by maximum static friction, especially in the initial landing roll after touchdown. Due to higher roll speeds and lift, the vertical load on the wheels is lower, resulting in less maximum static friction and even less deceleration from the wheel brakes. Therefore, aircraft are also equipped with drag chutes. The drag chute consists of a drag chute mechanism, transmission components, and signaling equipment. When the contact point between the slider and pulleys moves to the line connecting the centers of the two pulleys, the external force acting on the pawl cannot open the pawl; this position is called the true lock position. After the drag chute is inserted into the canopy, the hook automatically enters the false lock position. The drag chute serves as the primary deceleration and attitude stabilization mechanism for the aircraft, and also functions as the main parachute and guide chute. Ensuring reliable straightening of the guide chute is technically very challenging. Summary of the Invention

[0006] To overcome the shortcomings of existing buffers, this invention addresses the defects of existing mechanical spring-loaded devices, such as large impact at the opening end and short lifespan. It provides a torque direct-rotation spring-loaded buffer that can smoothly absorb the energy generated by the impact, has stable buffering force, reliable spring-loaded buffering, balanced resistance, long lifespan, large buffering capacity, balanced pressure, and stable buffering effect.

[0007] The technical solution adopted by this invention to solve the technical problem is: a hydraulic torque direct-rotation spring-loaded damper, comprising: a hydraulic cylinder 7 fixed to a port support by means of end rings and lugs; an outer cylinder 5 fixed to a trapezoidal support by means of end rings and sealing the hydraulic cylinder 7; and a direct-rotation piston rod 8 that rotates within the hydraulic cylinder 7. The outer cylinder 5 is characterized by having a damping adjuster 3 corresponding to a stop bushing 24 at its center, located on both sides of the damping adjuster 3 and surrounding the outer cylinder 5, constrained by a torsion spring pressure block 28. Left-hand and right-hand torsion springs 6 provide torsional torque; the damping adjuster 3 generates damping force through the damping hole 16 of the built-in damping element 15. The straight-rotating piston 20 slides back and forth along the cylinder wall towards the two damping chambers 12 separated by the stop bushing 24, generating a stabilizing motion. The pressure in the damping chamber 12 is pressed by the radial valve ball 26 on the stop bushing 24 against the annular groove flow channel 17 and the slotted flow channel 27, forming a one-way valve that closes the valve hole. The damping oil enters the bottom of the damping element 15 and flows along the wall of the hydraulic cylinder 7 through the throttling damping passage. The flow path is as follows: The straight-rotating piston rod 8 is sealed at both ends of the hydraulic cylinder 7, forming a damping cavity 12 with the center of the stop bushing 24, where the symmetrically separated straight-rotating pistons 20 and the Y-ring 18 axially embedded in the cage 22 are connected. At the same time, through the oil replenishing springs 9 encapsulated in the inner cavities at both ends of the hydraulic cylinder 7, two oil replenishing cavities 11 filled with hydraulic medium are formed between the spring seat plate 10 and the locking ball. The two left and right straight-rotating piston rods 8 compress the damping cavity through the two symmetrical straight-rotating pistons 20 on both sides of the stop bushing 24. 12 Internal damping oil balances the pressure of thermal expansion and contraction of hydraulic medium; it enters the two-sided oil replenishment chambers 11 through the slotted flow channel 27 and relies on hydraulic damping to buffer the mechanical switching equipment acting on it. The two straight-rotating pistons 20 rotate to a fixed angle and rely on the internal structure to provide torsional damping torque to transmit to the left and right torsion springs 6. The hydraulic rotation accelerates the rotation of the springs. The left and right torsion springs 6, which are pressed by the torsion spring pressure block 28 on the bolt 29, are buffered and relaxed under the action of torque to release the buffered switching equipment.

[0008] Compared with the prior art, the present invention has the following advantages:

[0009] The present invention employs a hydraulic cylinder 7 fixed to a port support by means of lugs at both ends, an outer cylinder 5 of the hydraulic cylinder 7 fixed to a trapezoidal support by means of lugs at both ends, and a straight-rotating piston rod 8 that rotates within the hydraulic cylinder 7. The structure is compact, has small dimensions, and has no installation direction requirements.

[0010] This invention employs two sets of buffering mechanisms with the same torque magnitude and direction, both possessing end-effector buffering functionality. These mechanisms simultaneously output buffering torque, which is twice the torque of a single-output buffer, resulting in superior buffering performance. Furthermore, they prevent structural deformation of mechanical switching equipment caused by asymmetrical buffering forces.

[0011] This invention employs torsion springs 6 symmetrically surrounding the damping adjuster on both sides of the outer cylinder 5, a hydraulic cylinder 7 sealed within the outer cylinder 5, a straight-rotating piston rod 8 sealed within the damping cavity of the hydraulic cylinder 7, a stop bushing 24 corresponding to the damping adjuster and symmetrically positioned at both ends of the stop bushing 24 on the middle of the straight-rotating piston rod 8, and straight-rotating pistons 20. After the mechanical switching device rotates to the final stage, the straight-rotating connecting pin is screwed into the final section of the spiral limiting groove of the straight-rotating piston 20 and the straight-rotating piston 8. The left and right rotating torsion springs cause the piston to return to its original position after completing the buffering action. The left and right replenishing oil springs play a buffering and acceleration role between the impact head and the piston. Therefore, the invention is reliable in operation, has balanced resistance, long service life, and stable buffering effect.

[0012] In this invention, the damping adjuster is fixed in the middle of the outer cylinder 5, and the torsion spring 6, which provides torque for opening the mechanical switch, is separated on both sides. The outer cylinder 5 with end caps is assembled in the damping adjuster cylinder by ring sealing. The adjusting screw 14 passes through the end cap hole of the outer cylinder 5 through the bottom end of the damping element 15, which has a throttling effect, and extends radially into the stop bushing 24 and is coupled to the straight-rotating piston rod 8. The buffer is adjusted by the adjusting bolt 14 that passes through the bottom end of the damping element 15 through the damping adjuster. Relying on the smooth buffering effect, the buffering efficiency and damping coefficient are greatly improved compared with the previous buffers.

[0013] In this invention, a rotary piston rod 8, rotating within the damping chamber of a hydraulic cylinder 7, is constrained by two symmetrical spring seat plates 10 and sealing rings on either side of two rotary pistons 20. These springs, which balance the thermal expansion and contraction pressure of the hydraulic medium, are placed within two replenishing chambers 11 filled with hydraulic medium. This causes the rotary pistons 20 to move towards the two chambers of the damping chamber 12 separated by a stop bushing 24. The two ends of the rotary pistons 20 compress the damping oil within the damping chambers 12, generating damping force through the damping holes 16. This method uses two variable-capacity chambers to respectively represent the rodless chamber of the piston rod and the variable chamber between the piston rod and the inner cylinder wall; and uses a constant-capacity chamber to represent the annular constant chamber between the inner and outer cylinder walls, achieving uniform speed buffering with a large buffering capacity, balanced pressure, and stable buffering effect. By utilizing the fluid's flow between a variable and a fixed volume within a closed cavity, and leveraging the fluid's incompressibility to achieve appropriate pressure bearing and buffering, the sealed fluid generates suitable buffer pressure. This pressure acts on the piston, ensuring that the buffer pressure within the cylinder remains constant during the buffering process, thus achieving uniform deceleration buffering. It not only smoothly absorbs the energy generated by impacts but also allows for customized buffering force design, ensuring stable and reliable operation. Therefore, it features adjustable damping torque, enabling the smooth absorption of impact energy.

[0014] This invention employs a rotating piston 20 that moves towards the two chambers of the damping cavity 12 separated by the stop bushing 24. The two rotating pistons 20 compress the damping oil in the damping cavity 12 at both ends, forming a damping force through the damping hole 16. The pressure in the damping cavity 12 causes the steel ball 26 to press tightly against the oil replenishing valve seat 25. The one-way valve closes, and the damping oil enters the bottom of the damping element 15 and flows along the throttling damping channel of the cylinder wall to the annular groove channel 17. It then enters the two oil replenishing chambers 11 through the slot channel 27 of the outer cylinder 5 and is transmitted to the mechanical switch device through the rotating piston rod 8. When the mechanical switch device is opened, the rotating piston 20 at the end compresses the damping cavity 12. The damping oil pressure causes the steel ball 26 to press tightly against the oil replenishing valve seat 25. The one-way valve closes, and after the locking hook 4 is opened, the mechanical switch device is opened by the torque of the rotating spring buffer 3. The rotating buffer 3 rotates to a fixed angle and relies on its internal structure to provide torsional damping torque, providing end buffering for the mechanical switch device. When the external force is absent, the spring will spring back to its starting point under the action of the piston. This application of hydraulic dampers to mechanical switching equipment can prevent excessive travel of the mechanical switching equipment. Compared with dampers made of traditional elastic elements (rubber blocks, spiral springs), hydraulic dampers have a large stroke, absorb more energy, can smoothly absorb the energy generated by impact, and provide stable and reliable buffering force.

[0015] Examples of applications of this invention include industries such as aviation, aerospace, and vehicles, and various types of pop-up doors, where it provides an end-of-screw buffer torque to reduce end-of-screw impact force and improve structural service life. Attached Figure Description

[0016] Figure 1 This is a front view of the hydraulic torque direct-rotation spring buffer of the present invention;

[0017] Figure 2 yes Figure 1 Sectional view along axis AA;

[0018] Figure 3 yes Figure 2 BB-direction sectional view;

[0019] Figure 4 yes Figure 2 CC-direction sectional view;

[0020] Figure 5 yes Figure 2 DD section view;

[0021] Figure 6 yes Figure 3 EE-directed sectional view;

[0022] Figure 7 This is a schematic diagram of an embodiment of the present invention assembled at the mounting position of the deceleration parachute door launcher;

[0023] Figure 8yes Figure 7 A magnified view of the area along direction A;

[0024] Figure 9 Figure 7 A magnified schematic diagram of the B-axis;

[0025] Figure 10 Yes, this is a magnified view of a portion of the image.

[0026] In the diagram: 1. Parachute compartment cylinder, 2. Parachute compartment cover, 3. Damping adjuster, 4. Locking hook, 5. Outer cylinder, 6. Left and right rotating torsion springs, 7. Hydraulic cylinder cylinder, 8. Straight-rotating piston rod, 9. Oil replenishing spring, 10. Spring seat plate, 11. Oil replenishing chamber, 12. Damping chamber, 13. End cap cylinder, 14. Adjusting screw, 15. Damping element, 16. Damping hole, 17. Annular groove flow channel, 18. Y-ring, 19. Straight-rotating connecting pin, 20. Straight-rotating piston, 21. Straight-moving connecting pin, 22. Cage, 23. Fixed connecting pin, 24. Stop bushing, 25. Oil replenishing valve seat, 26. Valve steel ball, 27. Slotted flow channel, 28. Torsion spring pressure block, 29. Bolt.

[0027] The embodiments and effects of the invention will be further described below with reference to the accompanying drawings. Implementation

[0028] See Figures 1-6In the preferred embodiment described below, a hydraulic torque linear retraction damper includes: a hydraulic cylinder 7 fixed to a port support by means of lugs at both ends, an outer cylinder 5 fixed to a trapezoidal support by means of lugs at both ends and sealing the hydraulic cylinder 7, and a linear piston rod 8 that rotates within the hydraulic cylinder 7. The outer cylinder 5 has a damping adjuster 3 corresponding to the stop bushing 24 in the middle. The damping adjuster 3 is located on both sides of the damping adjuster 3 and surrounds the outer cylinder 5. The left and right torsion springs 6, which are constrained on the torsion spring pressure block 28, provide torsional torque. The damping adjuster 3 generates damping force through the damping hole 16 of the built-in damping element 15. The straight-rotating piston 20 slides back and forth along the cylinder wall towards the two damping chambers 12 separated by the stop bushing 24 to generate a stabilizing motion. The pressure of the damping chamber 12 is pressed by the radial valve steel ball 26 on the stop bushing 24 to press the annular groove flow channel 17 and the slotted flow channel 27, forming a one-way valve that closes the valve hole. The damping oil enters the bottom of the damping element 15 and flows along the throttling damping channel of the hydraulic cylinder 7 hole wall. The straight-rotating piston rod 8 is sealed by the rings at both ends of the hydraulic cylinder 7. With the stop bushing 24 as the center, the straight-rotating piston 20, which is symmetrically separated at both ends, is axially embedded in the retaining ring. A damping cavity 12, a closed space, is formed between the Y-shaped rings 18 of the frame 22. At the same time, two oil replenishing cavities 11 filled with hydraulic medium are formed between the spring seat plate 10 and the locking ball through the oil replenishing springs 9 encapsulated in the inner cavities at both ends of the hydraulic cylinder 7. The two left and right straight-rotating piston rods 8 compress the damping oil in the damping cavity 12 through the two symmetrical straight-rotating pistons 20 on both sides of the stop bushing 24, balancing the pressure of thermal expansion and contraction of the hydraulic medium. The oil enters the oil replenishing cavities 11 on both sides through the double-divided oil passage of the slotted flow channel 27. The hydraulic damping buffers the mechanical switching equipment acting on it. When the two straight-rotating pistons 20 rotate to a fixed angle, the internal structure provides torsional damping torque, which is transmitted to the left and right torsion springs 6. The hydraulic rotation accelerates the rotation of the springs. The left and right torsion springs 6, which are pressed by the torsion spring pressure block 28 on the bolt 29, expand and spring open the buffered switching equipment under the action of torque.

[0029] The damping adjuster 3 includes: an end cap 13 screwed into the adjusting cylinder; an adjusting screw 14 sealed by the inner cylinder ring of the end cap 13; a damping element 15 screwed to the adjusting screw 14; the damping element 15 is a stepped cylinder with a damping hole 16 on the end face of the stepped cylinder; the adjusting screw 14 passes through the end cap hole and is connected to the inner thread hole of the damping element 15 through a stepped threaded rod; the stepped necked cylinder of the damping element 15 extends into the annular groove flow channel 17 and the damping cavity 12 formed between the outer cylinder 5 and the inner annular surface of the hydraulic cylinder 7; and a coupling stop bushing 24 is connected to a flow divider screw.

[0030] When the mechanical switch is closed, the rotary piston 20 moves towards the two oil replenishment chambers 11. The damping oil in the oil replenishment chambers 11 flows through the slotted flow channels 27 of the outer cylinders 5 on both sides to the annular flow channel 17. At this time, the steel ball 26 moves away from the oil replenishment valve seat 25, the check valve opens, and the damping oil flows back to the damping chamber 12 through the oil replenishment circuit. This process does not generate damping force; the mechanical switch only needs to overcome the torsional torque of the left and right rotary torsion springs 6 to close normally.

[0031] Furthermore, the two oil replenishing springs 9 mounted on the left and right sides of the straight-rotating piston rod 8 provide pre-pressure through the spring seat plate 10 and the sealing ring of the dynamic seal, respectively.

[0032] Furthermore, the hydraulic cylinder 7, Y-ring 18, and damping element 15, which are sealed in the outer cylinder 5, form a damping cavity 12. 0022. The straight-rotating piston rod 8 is divided into left and right sections. The left section is inserted into the right section's docking hole through a stepped docking shaft and is coaxially connected as one piece by a radial fixed connecting pin 23.

[0033] The damping element 15 and the end cap 13 are threadedly engaged. The bottom end of the damping element 15 is provided with a V-shaped oblique groove corresponding to the radial damping hole of the stop bushing 24. Rotating the adjusting bolt 14 drives the damping element 15 to rotate. By adjusting the lifting distance between the damping element 14 and the stop bushing 24, the opening of the V-shaped oblique groove and the radial damping hole can be adjusted, thereby realizing the damping torque adjustment function.

[0034] The free end of the adjusting bolt 14 has a slot for adjusting the damping element 15. One end of the damping element 15 extends into the stop bushing 24 and acts as a throttling device.

[0035] Furthermore, each straight-rotating piston 20 has a retainer 22 with a symmetrical stop bushing 24 on its inner end face. The retainer 22 is assembled in the annular groove of the straight-rotating piston rod 8 and fixed by the straight-rotating connecting pins 19 of the two radially symmetrical annular grooves. Each retainer 22 limits the rotational movement of the left and right straight-rotating pistons 20.

[0036] Each straight-rotating piston 20 has a retainer 22 with a symmetrical stop bushing 24 on its inner end face. The retainer 22 is assembled in the annular groove of the straight-rotating piston rod 8 and is fixed by the straight-rotating connecting pins 19 of the two radially symmetrical annular grooves. Each retainer 22 limits the rotational movement of the left and right straight-rotating pistons 20.

[0037] Each cage 22 has a Y-shaped sealing ring 18 on its inner end face pressure surface. The Y-shaped sealing ring adheres to the inner sealing mating surface of the cage 22 by its open lip. The bottom of the self-sealing lip ring is axially compressed, and the lip is circumferentially compressed, widening the contact with the sealing surface and increasing the contact stress. When the internal pressure increases further, the distribution and magnitude of the contact pressure change further, and the lip fits more tightly with the sealing surface, effectively sealing the 32MPa high pressure.

[0038] The hydraulic cylinder 7 is assembled in the outer cylinder 5 through a ring seal. The adjusting screw 14 passes through the end cap hole of the outer cylinder 5 and passes through the bottom end of the damping element 15, which plays a throttling role. It extends radially into the stop bushing 24 and is coupled to the straight-rotating piston rod 8. The stop bushing 24 forms a damping cavity 12 with a closed space between the straight-rotating piston 20 and the hydraulic cylinder 7, which are symmetrically separated at both ends. At the same time, the steel ball 26 is encapsulated in the radial oil replenishment valve seat 25 of the stop bushing 24 to form a one-way valve that guides throttling and reverses oil replenishment for the straight-rotating spring buffer 3.

[0039] The damping element 15 and the end cap 13 are threadedly engaged. The bottom end of the damping element 15 is provided with a V-shaped oblique groove corresponding to the radial damping hole of the stop bushing 24. Rotating the adjusting bolt 14 drives the damping element 15 to rotate. By adjusting the lifting distance between the damping element 14 and the stop bushing 24, the opening of the V-shaped oblique groove and the radial damping hole can be adjusted, thereby realizing the damping torque adjustment function.

[0040] The free end of the adjusting bolt 14 has a slot for adjusting the damping element 15. One end of the damping element 15 extends into the stop bushing 24 and acts as a throttling device.

[0041] See Figures 7-10 In the following optional embodiments, the parachute compartment consists of three parts: the compartment body, the door, and the door lock. The compartment body is cylindrical with a slight internal taper. The door is approximately hemispherical, hinged to the compartment body at the top and fitted with a door lock ring at the bottom. The door is positioned by a locking pin after opening. The door lock is located directly below the compartment opening and is encased in a fairing. The door lock consists of a locking hook, a stop arm, a locking rocker arm, an interlocking rocker arm, a crank, a spring, and a coordinating steel cable. When the door opens, the guide parachute with a helical compression spring is ejected. The parachute hook is the connection device between the deceleration parachute and the aircraft body. The hook is fixed to the deceleration parachute beam with two bolts, and its lower part is connected to the ground-launching mechanism of the door lock. The hook is in the unlocked position. The compression spring inside the actuating cylinder is compressed. The spring pushes the piston through the stop bushing, causing the slider to press against the pulley at the pawl tail. When the parachute is pushed into the parachute compartment, the hanging ring collides with the small claw of the hook, causing the hook to rotate and close, disengaging the tail pulley. Under the action of the compression spring, the stop bushing, piston, and slider move together to the right. The slider inserts between the two pulleys, driving the fork rocker arm assembly to rotate. When the stop bushing moves to the boss of the inner arm of the driven cylinder to limit movement, the piston and slider are limited by the limiting pin on the long rocker arm of the fork rocker arm assembly inserting into the hole on the housing, preventing the slider from exceeding the false lock position due to inertia.

[0042] When the check valve is closed, the damping oil enters the bottom of the damping element 15 and flows along the throttling damping channel of the cylinder wall to the annular groove channel 17. It then enters the two-sided oil replenishment chambers 11 through the straight-rotating piston rod 8 and is transmitted to the parachute cover 2. When the parachute cover 2 opens, the straight-rotating piston 20 compresses the damping chamber 12. The damping oil pressure causes the steel ball 26 to press tightly against the oil replenishment valve seat 25. When the check valve is closed and the locking hook 4 is opened, the parachute cover 2 is opened by the torque of the straight-rotating spring buffer 3. The straight-rotating buffer 3 rotates to a fixed angle and relies on its internal structure to provide torsional damping torque, reducing the opening speed of the parachute cover and providing end buffer for the parachute cover 2.

[0043] The locking hook 4 is installed on the pin of the parachute compartment 1 and can rotate around the pin. When the parachute compartment cover 2 is closed, the locking hook 4 hooks onto the locking ring on the cover 2, overcoming the torsional torque of the straight-rotating hydraulic damper 3, thus keeping the cover 2 closed. When the cover 2 is closed, the straight-rotating piston 20 moves towards the two end oil replenishment chambers 11. The damping oil in the replenishment chambers 11 flows through the slotted flow channels 27 of the outer cylinders 5 on both sides to the annular groove flow channel 17. At this time, the steel ball 26 moves away from the replenishment valve seat 25, the one-way valve opens, and the damping oil flows back to the damping chamber 12 through the replenishment oil circuit. This process does not generate damping force; the cover 2 only needs to overcome the torsional torque of the torsion spring 6 to close normally.

[0044] After the locking hook 4 disengages from the locking ring of the parachute compartment cover 2, the cover 2 springs open under the torsional force of the torsion spring 6. When the parachute compartment door opens, the pilot chute with a helical compression spring is deployed, pulling the main parachute and its sheath out of the compartment under aerodynamic force, and the main parachute then opens. The deployment method relies on the kinetic energy of the deployed parachute compartment cover to straighten the pilot chute, and then the aerodynamic force generated by the pilot chute pulls the drag chute or the main parachute. The parachute compartments are located on the side walls of the reentry capsule. The deployed parachute compartment cover sequentially connects to the pilot chute and the drag chute. The drag chute separates through the drag chute release mechanism, and then the main parachute is deployed. In the normal landing procedure, the parachute compartment cover drives the parachute pack, and the deployed parachute compartment cover pulls out the pilot chute and the drag chute. When the drag chute is used in conjunction with the wheel brake system, it can compensate for each other's weaknesses. To prevent the drag chute from contacting the runway and being damaged, the chute can also be jettisoned by the transmission of cold air. Cold air enters the deceleration chamber of the actuator cylinder through the deceleration inlet connector, pushing the piston and slider to move to the right from the dummy lock position, thus rotating the fork rocker arm assembly. When the slider continues to move to the right from the true lock position until the piston hits the true lock on the actuator cylinder housing, the deceleration chute is released through the transmission of the coordinating steel cable at the lower end of the long rocker arm of the fork rocker arm assembly, opening the deceleration compartment door lock and deploying the drogue chute.

[0045] The embodiments of the present invention have been described in detail above. Specific implementation methods have been used to illustrate the present invention. The description of the above embodiments is only for the purpose of helping to understand the method and device of the present invention. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the ideas of the present invention. Therefore, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A hydraulic torque and roll straight lift shock absorber comprising: A hydraulic cylinder (7) is fixed to a port support by two end rings, and an outer cylinder (5) of the hydraulic cylinder (7) is fixed to a trapezoidal support by two end rings. A straight-rotating piston rod (8) rotates within the hydraulic cylinder (7). The outer cylinder (5) has a damping adjuster (3) corresponding to a stop bushing (24) in the middle. Left and right torsion springs (6) are located on both sides of the damping adjuster (3) and surround the outer cylinder (5), and are constrained on a torsion spring block (28) to provide torsional torque. The damping adjuster (3) Damping force is generated through the damping hole (16) of the built-in damping element (15). The rotary piston (20) slides back and forth along the cylinder wall towards the two damping chambers (12) separated by the stop bushing (24), generating a stabilizing motion. The pressure in the damping chamber (12) is pressed tightly against the annular groove flow channel (17) and the slotted flow channel (27) by the radial valve ball (26) on the stop bushing (24), forming a one-way valve that closes the valve hole. The damping oil enters the bottom of the damping element (15) and flows along the throttling damping channel of the hydraulic cylinder barrel (7) hole wall. The rotary piston rod (8) passes through the hydraulic... The cylinder (7) is sealed at both ends with ring seals. Centered on the stop bushing (24), a damping cavity (12) is formed between the symmetrically separated straight-rotary pistons (20) and the Y-ring (18) axially embedded in the cage (22). Simultaneously, through the oil-replenishing springs (9) encapsulated in the inner cavities at both ends of the hydraulic cylinder (7), two oil-replenishing cavities (11) filled with hydraulic medium are formed between the spring seat plate (10) and the locking ball. The left and right straight-rotary piston rods (8) compress the damping cavity through the two symmetrically arranged straight-rotary pistons (20) on both sides of the stop bushing (24). 12) The internal damping oil balances the pressure of thermal expansion and contraction of the hydraulic medium. It enters the two-sided oil supply chambers (11) through the one-slot flow channel (27). It relies on hydraulic damping to buffer the mechanical switching equipment acting on it. The two straight pistons (20) rotate to a fixed angle and rely on the internal structure to provide torsional damping torque to the left and right torsion springs (6). The hydraulic rotation accelerates the rotation of the springs. The left and right torsion springs (6) pressed by the torsion spring pressure block (28) on the bolt (29) are buffered and relaxed under the action of torque to release the buffered switching equipment.

2. The hydraulic torque and direct rotation pop-up bumper of claim 1, wherein: The damping adjuster includes: an end cap (13) screwed into the adjusting cylinder, an adjusting screw (14) sealed by the inner cylinder ring of the end cap (13), a damping element (15) screwed to the adjusting screw (14), the damping element (15) being a stepped cylinder with a damping hole (16) on the end face of the stepped cylinder, the adjusting screw (14) passing through the end cap hole and connected to the inner thread hole of the damping element (15) through a stepped threaded rod, the stepped necking cylinder of the damping element (15) extending into the annular groove flow channel (17) and damping cavity (12) formed between the outer cylinder (5) and the inner annular surface of the hydraulic cylinder (7), and a coupling stop bushing (24) diverting screw.

3. The hydraulic torque and direct rotation pop-up bumper of claim 1, wherein: When the mechanical switch is closed, the straight-rotating piston (20) moves towards the two-end oil replenishment chambers (11). The damping oil in the oil replenishment chamber (11) flows through the slotted flow channel (27) of the outer cylinders (5) on both sides to the annular groove flow channel (17). At this time, the steel ball (26) moves away from the oil replenishment valve seat (25), the one-way valve opens, and the damping oil flows back to the damping chamber (12) through the oil replenishment oil circuit. This process will not generate damping force. The mechanical switch can be closed normally by overcoming the torsional torque of the left and right rotating torsion springs (6).

4. The hydraulic torque and direct rotation pop-up bumper of claim 1, wherein: The hydraulic cylinder (7), Y-ring (18), and damping element (15) sealed in the outer cylinder (5) form a damping cavity (12).

5. The hydraulic torque and direct rotation pop-up bumper of claim 1, wherein: The straight-rotating piston rod (8) is divided into left and right sections. The left section is inserted into the right section through the stepped docking shaft and is coaxially connected as one piece by the radial fixed connecting pin (23). The two oil replenishing springs (9) on the left and right sides of the straight-rotating piston rod (8) provide pre-pressure through the spring seat plate (10) and the sealing ring of the dynamic seal, respectively.

6. The hydraulic torque and direct rotation pop-up bumper of claim 1, wherein: Each straight-rotating piston (20) has a retainer (22) with a symmetrical stop bushing (24) on its inner end face. The retainer (22) is assembled in the annular groove of the straight-rotating piston rod (8) and fixed by a straight-rotating connecting pin (19) with two radially symmetrical annular grooves. Each retainer (22) limits the rotational movement of the left and right straight-rotating pistons (20).

7. The hydraulic torque and direct rotation pop-up bumper of claim 6, wherein: Each cage (22) is fitted with a Y-shaped ring (18) with a Y-shaped interface on the inner end face of the pressure surface. The Y-shaped sealing ring adheres to the inner sealing pair coupling surface of the cage (22) by relying on its open lip. The bottom of the self-sealing lip ring is axially compressed, and the lip is circumferentially compressed, which widens the contact with the sealing surface and increases the contact stress. When the internal pressure increases further, the distribution pattern and magnitude of the contact pressure change further, and the lip fits more tightly with the sealing surface, effectively sealing the high pressure of 32MPa.

8. The hydraulic torque and direct rotation pop-up bumper of claim 1, wherein: The hydraulic cylinder (7) is assembled in the outer cylinder (5) through a ring seal. The adjusting screw (14) passes through the end cap hole of the outer cylinder (5) and passes through the bottom end of the damping element (15) which plays a throttling role. It extends radially into the stop bushing (24) and is coupled to the straight-rotating piston rod (8). The stop bushing (24) forms a damping cavity (12) between the straight-rotating piston (20) and the hydraulic cylinder (7) that are symmetrically separated at both ends. At the same time, the steel ball (26) is encapsulated in the radial oil replenishment valve seat (25) of the stop bushing (24) to form a one-way valve for guiding throttling and reverse oil replenishment of the straight-rotating spring buffer.

9. The hydraulic torque and direct rotation pop-up bumper of claim 1, wherein: The damping element (15) and the end cap (13) are threaded meshing structures. The bottom end of the damping element (15) is provided with a V-shaped oblique groove corresponding to the radial damping hole of the stop bushing (24). Rotating the adjusting screw (14) drives the damping element (15) to rotate. By adjusting the lifting distance between the damping element (15) and the stop bushing (24), the opening of the V-shaped oblique groove and the radial damping hole can be adjusted to realize the damping torque adjustment function.

10. The hydraulic torque and direct rotation pop-up bumper of claim 1, wherein: The free end of the adjusting screw (14) has a slot for adjusting the damping element (15). One end of the damping element (15) is inserted into the stop bushing (24) to play a throttling role.

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