Damping hydraulic cylinder arrangement for offshore vertical launching device

Abstract

The present application relates to hydraulic buffering and damping technical field, disclose a damping hydraulic cylinder device for offshore vertical transmitting equipment, including cylinder, rodless end cover, rod end guide sealing assembly, piston rod, piston assembly, first oil port, second oil port, double threshold sequence buffering assembly and self-adapting backfill assembly, the cylinder is respectively sealed with the rodless end cover and the rod end guide sealing assembly at both ends Connection, the piston assembly is arranged in the cylinder and is connected with the piston rod, the piston assembly divides the cylinder internal space and forms the rodless chamber and the rod chamber.The present application makes the hydraulic cylinder realize the sequence switching from pre-buffering to main buffering at the end of stroke, and maintains the main buffering state after the mechanical pushing is weakened through the pressure memory chamber, and triggers the valve core reset and backfill opening by using the low pressure state of the local low pressure sensitive chamber, to realize the double threshold sequence control of high pressure trigger retention and low pressure trigger reset, to overcome the problems in the prior art.

Description

Technical Field

[0001] This invention relates to the field of hydraulic buffering and vibration reduction technology, and more specifically, to a vibration-damping hydraulic cylinder device for offshore vertical launch equipment. Background Technology

[0002] In actual use, maritime vertical launch systems are subjected to not only the swaying and heave of the ship caused by waves, but also random structural vibrations and transient impact loads from launch. These multi-source excitations can easily subject the buffer, support, or vibration damping mechanisms connected to the launch device to significant dynamic loads. Insufficient damping and buffering capacity can lead not only to rigid impacts and rebounds at the ends, but also to the transfer of impact energy to the main body of the vertical launch system and the ship's structure, thus affecting the equipment's reliability and lifespan.

[0003] Existing hydraulic cylinders often achieve end-of-stroke deceleration by setting a single-stage throttling buffer structure at the end of the stroke. The typical method is as follows: when the piston approaches the end, the buffer plunger enters the buffer sleeve to form a throttling gap, so that the hydraulic oil in the cylinder cavity is discharged through throttling and damping pressure is established to absorb the kinetic energy of the piston and load.

[0004] Currently, hydraulic cylinder devices still have the following shortcomings when facing transient impact conditions during launch from offshore vertical launch systems: 1. Under the transient impact of launch, the equivalent flow area of ​​the throttling channel changes rapidly. The fluid inertia and the sudden change in volume are superimposed, which can easily form pressure peaks and hydraulic shocks at the moment of buffer switching, namely the so-called water hammer phenomenon. 2. A single-stage buffer cannot simultaneously meet the needs of gradual pressure increase in the early stage and strong energy absorption in the later stage, which can easily lead to end-stage blockage, insufficient buffering, or aggravated rebound. 3. When the mechanical push of the buffer plunger weakens, the existing switching valve core or valve sleeve is prone to retract prematurely, resulting in insufficient maintenance of the main buffer state and causing the buffer pressure to oscillate or rebound. 4. When rebound or rapid depressurization occurs after the impact, the local area near the closed end of the buffer sleeve often experiences a pressure drop before the overall cylinder cavity, which in turn induces cavitation, gas mixing and a sudden drop in damping force, resulting in secondary impact and decreased buffer stability. Summary of the Invention

[0005] This invention provides a vibration-damping hydraulic cylinder device for offshore vertical launch equipment, which solves the technical problems in the related technology of single-stage throttling buffer structure of hydraulic cylinder that is prone to pressure spikes, water hammer, end jamming, insufficient main buffer maintenance, rebound, and local negative pressure cavitation during the rebound stage under high impact conditions of offshore vertical launch equipment.

[0006] The present invention provides a vibration damping hydraulic cylinder device for marine vertical launch equipment, including a cylinder barrel, a rodless end cap, a rod end guide sealing assembly, a piston rod, a piston assembly, a first oil port, a second oil port, a dual threshold sequential buffer assembly, and an adaptive recovery assembly.

[0007] The cylinder barrel is sealed to the rodless end cap and the rod end guide sealing assembly at both ends, respectively. The piston assembly is disposed inside the cylinder barrel and connected to the piston rod. The piston assembly divides the internal space of the cylinder barrel into a rodless chamber and a rod chamber. The first oil port is connected to the rodless chamber, and the second oil port is connected to the rod chamber.

[0008] The dual-threshold sequential buffer assembly includes a buffer plunger, a buffer sleeve, a valve seat, an axially movable sequential valve core, a return spring, a pre-buffered throttling channel, a main buffered throttling channel, an annular peak pressure chamber, a peak discharge branch, a pressure memory chamber, a memory pressurization one-way channel, a reset throttling channel, a low-pressure triggered reset valve, and a rapid pressure release channel. The buffer plunger is located on the rodless end of the piston assembly and is coaxially fixed to the piston assembly. The buffer sleeve is located inside the rodless end cap and is fixedly connected to the rodless end cap. At the end of its stroke, the buffer plunger enters the buffer sleeve to form an annular throttling gap. A buffer volume area is formed inside the buffer sleeve, and a local low-pressure sensitive cavity is formed between the axially inner side of the second throttling orifice group and the closed end of the buffer sleeve.

[0009] For example, in the method provided in at least one embodiment of this disclosure, the sequential valve core is disposed in the valve seat and can slide axially. The sequential valve core is provided axially in sequence with a first throttling orifice group for forming a pre-buffered flow path, a second throttling orifice group for forming a main buffered flow path, a peak discharge control shoulder, and a replenishment control window. An intermediate transition cavity is formed between the valve seat and the sequential valve core.

[0010] For example, in the method provided in at least one embodiment of this disclosure, the pressure memory chamber is formed on the side of the sequential valve core away from the buffer plunger; one end of the memory pressurization unidirectional channel is connected to the annular peak pressure chamber, and the other end is connected to the pressure memory chamber, so as to allow the pressure oil in the annular peak pressure chamber to enter the pressure memory chamber unidirectionally; the reset throttling channel is connected to the pressure memory chamber, so as to release the pressure oil in the pressure memory chamber at a limited flow rate; the control end of the low-pressure trigger reset valve is connected to the local low-pressure sensitive chamber, the inlet is connected to the pressure memory chamber, and the outlet is connected to the rapid pressure relief channel, so as to open the rapid pressure relief of the pressure memory chamber when the pressure in the local low-pressure sensitive chamber drops to a predetermined low-pressure threshold.

[0011] For example, in the method provided in at least one embodiment of this disclosure, the end of the sequential valve core facing the buffer plunger is provided with an inner conical force-bearing section, and the end of the buffer plunger is provided with an outer conical pushing section that cooperates with the inner conical force-bearing section, so that the sequential valve core moves from the initial position to the main buffer position under the mechanical pushing action of the buffer plunger; and pressurizes the pressure memory chamber through the memory pressurization one-way channel at the moment of main buffer switching, so that the sequential valve core is still held in the main buffer position for a predetermined time by the pressure memory chamber after the mechanical pushing is weakened.

[0012] For example, in the method provided in at least one embodiment of this disclosure, when the sequential valve core is in the initial position, the buffer volume area discharges oil through the first throttling orifice group, the intermediate transition cavity, and the pre-buffered throttling channel; when the sequential valve core is in the main buffer position maintained by the pressure memory cavity, the connection of the first throttling orifice group is blocked or reduced, and the buffer volume area discharges oil through the second throttling orifice group, the intermediate transition cavity, and the main buffered throttling channel.

[0013] For example, in the method provided in at least one embodiment of this disclosure, the annular peak pressure chamber is connected to the buffer volume area through a radial guide hole, and the peak discharge branch includes a peak discharge check valve, a flow limiting orifice, and a return oil channel; the peak discharge control shoulder on the sequence valve core cooperates with the valve seat to form a peak discharge displacement window, so that the peak discharge branch is only opened when the sequence valve core is in the main buffer position and the pressure of the annular peak pressure chamber reaches the opening threshold of the peak discharge check valve, so as to implement time-limited diversion and peak discharge on the pressure rise edge at the moment of main buffer switching.

[0014] For example, in the method provided in at least one embodiment of this disclosure, the adaptive replenishment component includes a replenishment reservoir, a replenishment oil circuit, an anti-cavitation check valve, and a replenishment flow restrictor. The replenishment reservoir is connected to the downstream of the peak discharge branch and / or the low-pressure section on the return oil side of the first oil port. One end of the replenishment oil circuit is connected to the replenishment reservoir or the low-pressure oil source, and the other end is connected to the local low-pressure sensitive cavity. The anti-cavitation check valve is disposed on the replenishment oil circuit and its opening direction is from the replenishment reservoir or the low-pressure oil source to the local low-pressure sensitive cavity. The replenishment control window on the sequence valve core forms an alignment connection with the valve seat after the pressure memory cavity is depressurized through the reset throttling channel and / or the rapid pressure relief channel, and during the return reset process of the sequence valve core, so that the replenishment oil circuit is selectively connected to the local low-pressure sensitive cavity, thereby implementing adaptive fixed-point replenishment of the local low-pressure sensitive cavity during the rebound or depressurization stage.

[0015] The beneficial effects of this invention are as follows: 1. By setting up a pressure memory chamber, a memory pressurization one-way channel, and a reset throttling channel, the sequential valve core forms a hydraulic self-holding triggered by high pressure after the main buffer switching, which can avoid the buffer pressure oscillation caused by the valve core retracting prematurely after the mechanical push weakens; 2. By setting a low-pressure trigger reset valve and a rapid pressure relief channel, the reset of the sequence valve core is no longer determined solely by a fixed time constant, but is instead bound to the actual pressure state of the local low-pressure sensitive chamber, forming a dual-threshold sequence control of high-pressure trigger holding and low-pressure trigger reset; 3. The peak relief branch is not a simple overpressure protection branch, but is bound to the main buffer holding state of the sequence valve core. It is only opened for a limited time during the high-risk period when the main buffer switches, and the pressure rise is specifically suppressed. 4. The backfill control window is not open at all times, but only when the local low-pressure sensitive cavity reaches the predetermined low-pressure threshold and triggers the sequential valve core return reset, thus forming a sequential action of "main buffer first, low-pressure trigger reset later, and fixed-point backfill following". 5. At least a portion of the oil diverted through the peak discharge branch can enter the replenishment storage chamber and serve as the preferred replenishment oil source during the rebound stage, thus enabling peak discharge and replenishment to form a cross-stage succession relationship in terms of oil circuit function. 6. Adaptive fixed-point replenishment is implemented for the local low-pressure sensitive cavity on the inner side of the second throttling orifice group, which can suppress local negative pressure, cavitation and gas mixing faster than conventional overall oil replenishment, and improve the stability of the buffer curve. 7. By using sequential coordinated control of "pre-buffered pressure increase, main buffer high pressure maintenance, timed peak discharge during switching, low pressure triggering reset, and adaptive fixed-point replenishment during the rebound stage", the risks of end jamming, rebound, water hammer and secondary impact are reduced, and the buffering reliability and service life of the hydraulic cylinder are improved.

[0016] In summary, this invention provides a hydraulic cylinder system for vibration reduction in offshore vertical launch equipment. The system enables the hydraulic cylinder to sequentially switch from pre-buffering to main buffering at the end of its stroke. The main buffering state is maintained by a pressure memory chamber after mechanical pushing weakens. Simultaneously, the low-pressure state of a local low-pressure sensitive chamber triggers valve core reset and recovery opening, achieving dual-threshold sequential control of high-pressure triggering and low-pressure triggering. This overcomes the problems of pressure spikes, water hammer, end jamming, insufficient main buffering maintenance, rebound, and localized negative pressure cavitation during the rebound stage that are easily generated in the existing single-stage throttling buffer structure of the hydraulic cylinder under high-impact conditions in offshore vertical launch equipment. Attached Figure Description

[0017] Figure 1 This is a partial cross-sectional structural schematic diagram of a vibration-damping hydraulic cylinder device for marine vertical launch equipment according to the present invention; Figure 2 This is a schematic diagram of the assembly and use structure of a vibration-damping hydraulic cylinder device for marine vertical launch equipment according to the present invention; Figure 3 This is a half-sectional structural diagram of the initial state of a vibration damping hydraulic cylinder device for marine vertical launch equipment according to the present invention. Figure 4This is a half-sectional structural diagram of the buffer state of a vibration damping hydraulic cylinder device for marine vertical launch equipment according to the present invention. Figure 5 This is a half-sectional structural diagram of the reset state of a vibration damping hydraulic cylinder device for marine vertical launch equipment according to the present invention. Figure 6 This is a schematic diagram of the assembly of a buffer plunger and a sequence valve core in a vibration-damping hydraulic cylinder device for marine vertical launch equipment according to the present invention.

[0018] In the diagram: 1. Cylinder; 2. Rodless end cap; 3. Rod end guide seal assembly; 4. Piston rod; 5. Piston assembly; 6. Rodless chamber; 7. Rod chamber; 8. First oil port; 9. Second oil port; 10. Buffer plunger; 11. Buffer sleeve; 12. Buffer volume area; 13. Valve seat; 14. Sequence valve core; 15. Return spring; 16. First throttling orifice group; 17. Second throttling orifice group; 18. Pre-buffered throttling channel; 19. Main buffered throttling channel; 20. Annular peak pressure chamber; 21. Radial guide orifice; 22. Peak venting check valve; 23. Flow limiting orifice; 24. Return 25. Oil passage; 26. Replenishment oil circuit; 27. Anti-cavitation check valve; 28. Replenishment flow limiting orifice; 29. ​​Local low-pressure sensitive chamber; 30. Pressure memory chamber; 31. Memory pressurization one-way channel; 32. Reset throttling channel; 33. Outer conical surface push section; 34. Inner conical surface force section; 35. Peak venting control shoulder; 36. Replenishment control window; 37. Replenishment oil storage chamber; 38. Initial limit shoulder; 39. Main buffer limit shoulder; 40. Replenishment alignment limit part; 41. Differential pressure drive end face; 42. Intermediate transition chamber; 43. Low-pressure trigger reset valve; 44. Rapid pressure relief channel. Detailed Implementation

[0019] The subject matter described herein will now be discussed with reference to exemplary embodiments. It should be understood that these embodiments are discussed only to enable those skilled in the art to better understand and implement the subject matter described herein, and changes may be made to the function and arrangement of the elements discussed without departing from the scope of this specification. Various processes or components may be omitted, substituted, or added as needed in the examples. Furthermore, some features described in the examples may be combined in other examples.

[0020] At least one embodiment of the present invention discloses a vibration-damping hydraulic cylinder device for offshore vertical launch systems, such as... Figure 1 As shown, to clearly define the installation position and direction of movement of each component, a right-handed rectangular coordinate system is first established: with the central axis of the hydraulic cylinder as the X-axis, the positive direction of the X-axis points from the rodless end to the rod end; Figure 1 Within the partial sectional view plane, the vertically upward direction is defined as the positive Y-axis; perpendicular to... Figure 1 The outward direction of the local section plane is defined as the positive direction of the Z-axis.

[0021] In the following descriptions, "axial" refers to the X-direction, "radial" refers to the YZ plane direction perpendicular to the X-axis, and "circumferential" refers to the circumferential distribution direction around the X-axis. Unless otherwise specified, the central axis of each cylindrical, annular, and hole-group part coincides with or is parallel to the X-axis.

[0022] In this coordinate system, cylinder 1 is a hollow cylindrical body extending along the x-axis; rodless end cap 2 is fixedly connected to the rodless end of cylinder 1, i.e., located at the negative x-axis end of cylinder 1; rod end guide sealing assembly 3 is fixedly connected to the rod end of cylinder 1, i.e., located at the positive x-axis end of cylinder 1; piston rod 4 passes through rod end guide sealing assembly 3 and is arranged along the x-axis; piston assembly 5 is fixed to the rodless end side of piston rod 4 and located inside cylinder 1, and a dynamic seal is formed between the outer cylindrical surface of piston assembly 5 and the inner cylindrical surface of cylinder 1, thereby dividing the interior of cylinder 1 along the x-axis into a rodless cavity 6 located on the rodless end side and a rod cavity 7 located on the rod end side. A first oil port 8 is provided on the rodless end cap 2 and communicates with the rodless cavity 6 after opening from the rodless end cap 2 along the y-direction and / or z-direction; a second oil port 9 is provided on the rod end guide sealing assembly 3 and / or the part of cylinder 1 near the rod end, and communicates with the rod cavity 7 radially from the outer periphery.

[0023] like Figures 1-6 As shown, the key structures of this invention are concentrated inside the rodless end cap 2, mainly including a dual-threshold sequential buffer assembly and an adaptive refill assembly; wherein, the dual-threshold sequential buffer assembly includes a buffer plunger 10, a buffer sleeve 11, a sequential valve core 14, a pre-buffered throttling channel 18, a main buffered throttling channel 19, an annular peak pressure chamber 20, a peak discharge branch, a pressure memory chamber 29, a memory pressurization one-way channel 30, a reset throttling channel 31, a low-pressure triggered reset valve 42, and a rapid pressure relief channel 43; wherein, the adaptive refill assembly includes a refill oil storage chamber 36, a refill oil circuit 25, and an anti-cavitation one-way valve 26.

[0024] A buffer sleeve 11 is coaxially disposed within the rodless end cap 2 along the x-axis. The open end of the buffer sleeve 11 faces the rod end, i.e., towards the positive x-axis direction, while the closed end of the buffer sleeve 11 is close to the inner wall of the rodless end cap 2, i.e., located on the negative x-axis side. A buffer plunger 10 is fixedly disposed in the center region of the rodless end face of the piston assembly 5 and extends along the x-axis towards the rodless end, such that when the piston assembly 5 moves towards the rodless end, the buffer plunger 10 is inserted into the buffer sleeve 11 from the open end along the negative x-axis direction. An annular gap is formed between the outer cylindrical surface of the buffer plunger 10 and the inner cylindrical surface of the buffer sleeve 11, and this annular gap is continuously distributed circumferentially along the yz plane. The end face of the buffer plunger 10, the inner wall of the closed end of the buffer sleeve 11, and the annular gap between them together form a buffer volume area 12.

[0025] More specifically, the locally enclosed region located on the negative x-axis side of the second throttling orifice group 17 and between the closed end of the buffer sleeve 11 and the corresponding flow passage section of the second throttling orifice group 17 constitutes a locally low-pressure sensitive cavity 28. Therefore, the locally low-pressure sensitive cavity 28 is spatially located inside the buffer sleeve 11, close to the closed end, and on the axial inner side of the second throttling orifice group 17.

[0026] The local low-pressure sensitive cavity 28 is a local cavity located between the inner side of the second throttling orifice group 17 and the closed end of the buffer sleeve 11. During the main buffer switching and rebound depressurization process, the local cavity experiences a pressure drop before the rest of the buffer volume area and serves as the pressure detection source for the low-pressure trigger reset valve 42. At the corresponding position on the outer periphery of the buffer sleeve 11, a valve cavity extending along the x-axis is formed inside the rodless end cap 2. The valve seat 13 is fixedly installed in this valve cavity and is arranged coaxially with the buffer sleeve 11. The sequence valve core 14 is disposed in the valve seat 13 and can slide back and forth relative to the valve seat 13 along the x-axis. The return spring 15 is disposed along the x-axis between the return side of the sequence valve core 14 and the valve seat 13, and is used to bias the sequence valve core 14 into the initial position. An annular gap is formed between the outer peripheral surface of the sequence valve core 14 and the inner bore surface of the valve seat 13. This annular gap closes around the x-axis in the yz plane and forms an intermediate transition cavity 41. The first throttling orifice group 16, the second throttling orifice group 17, the peak venting control shoulder 34, and the replenishment control window 35 are all formed on the outer peripheral wall of the sequential valve core 14 and are arranged sequentially at intervals along the x-axis. The first throttling orifice group 16 is located on the side closest to the buffer plunger 10, the second throttling orifice group 17 is located on the negative x-axis side of the first throttling orifice group 16, the peak venting control shoulder 34 is located on the negative x-axis side of the second throttling orifice group 17, and the replenishment control window 35 is located in the area between or near the second throttling orifice group 17 and the peak venting control shoulder 34. The first throttling orifice group 16 and the second throttling orifice group 17 are preferably evenly distributed circumferentially along the sequential valve core 14, with multiple orifices distributed around the x-axis on the same axial section to obtain approximately consistent throttling characteristics at each circumferential position.

[0027] The end of the sequence valve core 14 facing the buffer plunger 10 forms an inner conical force-bearing section 33, which is located at the positive x-axis end of the sequence valve core 14. The free end of the buffer plunger 10 forms an outer conical pushing section 32, which is located at the end of the buffer plunger 10 closest to the rodless end. When the piston assembly 5 continues to move toward the rodless end, the outer conical pushing section 32 and the inner conical force-bearing section 33 come into contact along the x-axis and form a progressive pushing motion, causing the sequence valve core 14 to switch displacement from the initial position to the main buffer position in the x-axis direction. To limit the start, end, and window position of the displacement, the valve seat 13 is preferably provided with an initial limiting shoulder 37, a main buffer limiting shoulder 38, and a return alignment limiting part 39. The initial limiting shoulder 37 is located at the x-axis end corresponding to the initial stopping position of the sequence valve core 14, the main buffer limiting shoulder 38 is located at the x-axis end corresponding to the main buffer holding position of the sequence valve core 14, and the return alignment limiting part 39 corresponds to the alignment position when the return control window 35 is connected to the local low pressure sensitive cavity 28.

[0028] A pressure memory chamber 29 is formed on the side of the sequence valve core 14 away from the buffer plunger 10, i.e., at the negative x-axis end of the sequence valve core 14. The pressure memory chamber 29 acts on the differential pressure drive end face 40 of the sequence valve core 14, which is the effective area of ​​the sequence valve core 14 under pressure on the negative x-axis side. The annular peak pressure chamber 20 is located on the circumferentially outer side or circumferentially adjacent to the closed end of the buffer sleeve 11, preferably an annular cavity closed around the x-axis. It is connected to the buffer volume area 12 through multiple radial guide holes 21. Each radial guide hole 21 extends from the buffer volume area 12 along the y-direction, z-direction, or radially obliquely relative to the x-axis to the annular peak pressure chamber 20, so that the local peak pressure in the buffer volume area 12 can be quickly transmitted to the annular peak pressure chamber 20. One end of the memory pressurization unidirectional channel 30 is connected to the annular peak pressure chamber 20, and the other end is connected to the pressure memory chamber 29. Its axis can be arranged along the x-direction, y-direction, z-direction, or a combination thereof, but the flow direction is limited to allow only the pressurized oil in the annular peak pressure chamber 20 to enter the pressure memory chamber 29. One end of the reset throttling channel 31 is connected to the pressure memory chamber 29, and the other end leads to the low-pressure side, the return oil side, or the return oil side passage of the first oil port 8. Its channel axis is usually arranged along the y-direction or z-direction, and it is used to implement restricted pressure relief of the pressure memory chamber 29.

[0029] The low-pressure trigger reset valve 42 is disposed inside the rodless end cap 2, preferably on the outside of the valve seat 13 or in its adjacent area. Its control end is connected to the local low-pressure sensitive chamber 28 through an independent control channel, the valve inlet is connected to the pressure memory chamber 29, and the valve outlet is connected to the rapid pressure relief channel 43. The rapid pressure relief channel 43 extends from the low-pressure trigger reset valve 42 along the y-direction, z-direction, and / or x-direction zigzag lines to the low-pressure return oil region, and its equivalent flow capacity is greater than that of the reset throttling channel 31. Thus, before the pressure in the local low-pressure sensitive chamber 28 drops to a predetermined threshold, the low-pressure trigger reset valve 42 remains closed, and the pressure memory chamber 29 can only be slowly depressurized through the reset throttling channel 31; when the pressure in the local low-pressure sensitive chamber 28 drops to the predetermined low-pressure threshold, the low-pressure trigger reset valve 42 opens, allowing the pressure memory chamber 29 to be rapidly depressurized through the rapid pressure relief channel 43, thereby triggering the sequence valve core 14 to quickly return and reset.

[0030] Both the pre-buffered throttling channel 18 and the main buffered throttling channel 19 are located inside the rodless end cap 2. Their axes can be arranged parallel to the x-axis and then connected to the intermediate transition cavity 41 via a transition hole, or they can be mainly located along the y-direction or z-direction. However, both are connected to the intermediate transition cavity 41 and the return oil side passage of the first oil port 8, respectively. The pre-buffered throttling channel 18 spatially corresponds to the alignment area of ​​the first throttling orifice group 16, and the main buffered throttling channel 19 spatially corresponds to the alignment area of ​​the second throttling orifice group 17. The equivalent throttling area of ​​the pre-buffered throttling channel 18 is larger than that of the main buffered throttling channel 19. Therefore, when the sequence valve core 14 is in the initial position, the first throttling orifice group 16 and the pre-buffered throttling channel 18 form the main flow path through the intermediate transition cavity 41; when the sequence valve core 14 switches to the main buffer position, the first throttling orifice group 16 deviates from or is blocked relative to the intermediate transition cavity 41, and the second throttling orifice group 17 and the main buffered throttling channel 19 form the main flow path through the intermediate transition cavity 41.

[0031] The peak-relief check valve 22, the flow-limiting orifice 23, and the return oil passage 24 together constitute the peak-relief branch. The peak-relief check valve 22 is preferably located inside the rodless end cap 2, near the annular peak pressure chamber 20. The flow-limiting orifice 23 is located downstream of the peak-relief check valve 22, and the return oil passage 24 is located downstream of the flow-limiting orifice 23 and leads to the return oil side passage of the first oil port 8 or the replenishment oil storage chamber 36. The peak-relief control shoulder 34 is formed on the outer periphery of the sequence valve core 14. When the sequence valve core 14 moves to the main buffer holding position, a peak-relief displacement window is formed between the peak-relief control shoulder 34 and the inner wall of the valve seat 13, which is only conductive in this axial position, establishing a displacement-controlled conductive relationship between the annular peak pressure chamber 20 and the peak-relief check valve 22.

[0032] The replenishment reservoir 36 in the adaptive replenishment assembly is preferably located inside the rodless end cap 2, in an independent reservoir located outside the sequence valve core 14, and is spatially adjacent to or directly connected to the downstream of the peak discharge branch, so that at least a portion of the oil diverted through the peak discharge branch during the main buffer switching can enter the replenishment reservoir 36. One end of the replenishment oil passage 25 is connected to the replenishment reservoir 36 or the low-pressure oil source, and the other end extends along the y, z, and / or x directions to the local low-pressure sensitive cavity 28; the anti-cavitation check valve 26 is connected in series on the replenishment oil passage 25, and its conduction direction is from the replenishment reservoir 36 or the low-pressure oil source to the local low-pressure sensitive cavity 28; the replenishment flow limiting orifice 27 is located upstream or downstream of the anti-cavitation check valve 26 to limit the replenishment flow. The replenishment control window 35 is located on the side of the sequence valve core 14 near the second throttle orifice group 17. When the sequence valve core 14 returns to the predetermined alignment position, the replenishment control window 35 is aligned with the inlet of the local low-pressure sensitive cavity 28 in the x-axis direction, thereby selectively connecting the replenishment oil circuit 25 with the local low-pressure sensitive cavity 28.

[0033] In a more specific embodiment, both the first throttling orifice group 16 and the second throttling orifice group 17 are composed of multiple through holes spaced apart circumferentially along the sequential valve core 14. These through holes are uniformly distributed around the x-axis on the same or adjacent axial sections, and the first throttling orifice group 16 and the second throttling orifice group 17 are spaced apart from each other in the x-axis direction. Preferably, the total equivalent flow area of ​​the first throttling orifice group 16 is greater than the total equivalent flow area of ​​the second throttling orifice group 17, and / or the single-hole diameter of the first throttling orifice group 16 is greater than the single-hole diameter of the second throttling orifice group 17, so as to establish a gentler pressure rise during the pre-buffering stage and form a stronger energy-absorbing throttling during the main buffering stage.

[0034] In a more specific embodiment, the intermediate transition cavity 41 between the outer periphery of the sequence valve core 14 and the inner hole of the valve seat 13 is not fixed to be connected to only a single channel, but rather, depending on the position of the sequence valve core 14 in the x-axis direction, it selectively connects to the pre-buffered throttling channel 18, the main buffered throttling channel 19, the peak discharge branch, and the return oil passage 25 in sequence. Specifically, when the sequence valve core 14 is in the initial position, the intermediate transition chamber 41 is preferentially connected to the first throttling orifice group 16 and the pre-buffered throttling channel 18; when the sequence valve core 14 switches to the main buffer position, the intermediate transition chamber 41 is preferentially connected to the second throttling orifice group 17 and the main buffered throttling channel 19; when the sequence valve core 14 is in the main buffer holding position and the peak discharge control shoulder 34 and the valve seat 13 form a peak discharge displacement window, the pressure state corresponding to the intermediate transition chamber 41 works in coordination with the peak discharge branch; when the sequence valve core 14 returns to the replenishment alignment position, the replenishment control window 35 is aligned with the local low-pressure sensitive chamber 28, so that the replenishment oil circuit 25 is connected to the local low-pressure sensitive chamber 28 through the relevant connecting channel.

[0035] In a more specific embodiment, the memory pressurization one-way channel 30 is internally equipped with a one-way valve core, a one-way steel ball, or an equivalent check structure, which allows only the pressurized oil in the annular peak pressure chamber 20 to rapidly enter the pressure memory chamber 29, while preventing the oil in the pressure memory chamber 29 from flowing back into the annular peak pressure chamber 20. The reset throttling channel 31 is preferably formed by a small-diameter throttling orifice, a slender throttling groove, or a combination of both, and its flow capacity is less than that of the memory pressurization one-way channel 30, thereby forming the delayed pressure relief required for hydraulic self-holding after the main buffer switching; the rapid pressure relief channel 43 is preferably formed by a channel with a cross-sectional area larger than that of the reset throttling channel 31, and its flow capacity is greater than that of the reset throttling channel 31, which can quickly release the pressurized oil in the pressure memory chamber 29 after the low-pressure trigger reset valve 42 is opened.

[0036] In a more specific embodiment, the differential pressure drive end face 40 is formed by a stepped end face of the sequence valve core 14 on the side opposite to the buffer plunger 10. This end face is positioned opposite the pressure memory chamber 29 and is pressurized in a direction perpendicular to the x-axis. The axial hydraulic pressure generated by the pressurized oil in the pressure memory chamber 29 acting on the differential pressure drive end face 40 is balanced by the reset force of the return spring 15 and other hydraulic pressures on the sequence valve core 14. This balances the sequence valve core 14 in the main buffer holding position even after the mechanical push of the buffer plunger 10 weakens, until the pressure in the local low-pressure sensitive chamber 28 drops to the opening threshold of the low-pressure trigger reset valve 42.

[0037] In a more specific embodiment, the annular peak pressure chamber 20 is connected to the buffer volume area 12 through multiple radially spaced radial guide holes 21. The peak discharge check valve 22 adopts a spring-preloaded check valve structure, and its valve core opens from the annular peak pressure chamber 20 to the return oil channel 24. The flow limiting hole 23 is located downstream of the peak discharge check valve 22 to limit the peak discharge flow rate per unit time, so as to avoid excessive peak discharge action and weaken the main buffer energy absorption. The return oil channel 24 can be directly connected to the return oil side passage of the first oil port 8, or it can be connected to the replenishment oil storage chamber 36 first, so that at least a portion of the oil diverted from the peak discharge branch enters the replenishment oil storage chamber 36 and constitutes the priority oil source for subsequent fixed-point replenishment.

[0038] In a more specific embodiment, the refill flow limiting orifice 27 is located downstream of the anti-cavitation check valve 26 and closer to the local low-pressure sensitive cavity 28. The refill control window 35 is located on the side of the sequence valve core 14 near the second throttling orifice group 17, so that when the sequence valve core 14 is triggered to return to its original position via the rapid pressure relief channel 43, the refill control window 35 preferentially forms axial alignment communication with the inlet of the local low-pressure sensitive cavity 28. By arranging the refill flow limiting orifice 27 closer to the local low-pressure sensitive cavity 28, the sudden increase in refill flow can be further suppressed, and the smoothness of the refill process can be improved.

[0039] In a more specific embodiment, the initial limiting shoulder 37, the main buffer limiting shoulder 38, and the return alignment limiting part 39 can be formed by the stepped surface of the inner hole of the valve seat 13, the shoulder surface, or the limiting ring. The initial limiting shoulder 37 is used to limit the initial stopping position of the sequence valve core 14 in the pre-buffering stage; the main buffer limiting shoulder 38 is used to limit the maximum main buffer displacement of the sequence valve core 14 in the high-pressure trigger holding stage; the return alignment limiting part 39 is used to limit the optimal alignment position of the return control window 35 and the local low-pressure sensitive cavity 28 when the sequence valve core 14 returns, thereby improving the repeatability of each operating position.

[0040] The working process of the hydraulic cylinder system of this invention is as follows: 1. Pre-buffering stage: Under the transient impact of launch, the piston assembly 5 moves rapidly towards the rodless end. When the buffer plunger 10 just enters the buffer sleeve 11, the sequence valve core 14 maintains its initial position under the action of the return spring 15. The oil in the buffer volume area 12 is mainly discharged through the first throttling orifice group 16, the intermediate transition chamber 41, and the pre-buffering throttling channel 18. Since the equivalent throttling area of ​​the pre-buffering throttling channel 18 is relatively large, this stage can first establish a relatively gentle damping climb process, reducing the initial steep pressure rise trend.

[0041] 2. Main Buffer Switching and High-Pressure Trigger Holding Stage: As the piston assembly 5 continues to move towards the rodless end, the outer conical pushing section 32 on the buffer plunger 10 gradually presses against the inner conical force-bearing section 33 on the sequence valve core 14, causing the sequence valve core 14 to receive a progressive axial mechanical thrust and move from its initial position to the main buffer position. At the moment of main buffer switching, the pressure in the annular peak pressure chamber 20 rises rapidly, and the pressure oil enters the pressure memory chamber 29 through the memory charging one-way channel 30, acting on the differential pressure drive end face 40, so that the sequence valve core 14 remains in the main buffer position after the mechanical pushing weakens. Since the low-pressure trigger reset valve 42 remains closed at this time, the pressure oil in the pressure memory chamber 29 can only be slowly released through the reset throttling channel 31, thus forming a main buffer holding state triggered by high pressure, avoiding pressure rebound and buffer instability caused by premature valve core retraction.

[0042] 3. Main Buffer Holding and Time-Limited Peak Relief Stage: During the main buffer holding stage, the second throttling orifice group 17 becomes the main flow path. The oil in the buffer volume area 12 is mainly discharged through the second throttling orifice group 17, the intermediate transition chamber 41, and the main buffer throttling channel 19, forming stronger energy absorption to avoid end jamming and excessive rebound. If a steep pressure rise occurs at the moment of main buffer switching or in the initial stage of main buffer, the pressure in the buffer volume area 12 is transmitted to the annular peak pressure chamber 20 through the radial guide orifice 21. At this time, the peak relief branch is briefly opened only when the sequence valve core 14 is held in the main buffer position and the pressure in the annular peak pressure chamber 20 reaches the opening threshold of the peak relief check valve 22, diverting part of the high-pressure oil through the flow limiting orifice 23 to the return oil channel 24 and / or back to the replenishment oil storage chamber 36. After the pressure drops, the peak relief branch is closed.

[0043] 4. Low-pressure trigger reset and adaptive fixed-point replenishment stage: During the rebound or reversal process after the impact, the local low-pressure sensitive chamber 28 experiences a pressure drop before other areas. When the local pressure drops to the predetermined low-pressure threshold, the low-pressure trigger reset valve 42 opens. The pressure oil in the pressure memory chamber 29 is slowly released through the reset throttling channel 31 and then rapidly released through the rapid pressure relief channel 43, causing the sequence valve core 14 to begin its return reset under the action of the reset spring 15. At this time, the replenishment control window 35 on it forms a positioning connection with the local low-pressure sensitive chamber 28. The oil in the replenishment oil storage chamber 36 or the oil in the low-pressure oil source is directly replenished into the local low-pressure sensitive chamber 28 through the anti-cavitation check valve 26 and the replenishment flow limiting orifice 27. Since the replenishment target is the local low-pressure sensitive chamber 28 rather than the entire rodless chamber 6, and the replenishment action is triggered by the local low-pressure state, the duration of negative pressure can be shortened, and premature oil replenishment can be avoided to weaken the main buffer energy absorption.

[0044] Through the aforementioned structural coordination, this invention divides the end-buffering process into four interconnected stages: pre-buffering, main buffer switching and high-pressure trigger holding, main buffer holding and time-limited peak venting, and low-pressure trigger reset and adaptive fixed-point replenishment. Specifically, the pre-buffering stage smoothly establishes damping and reduces the pressure rise slope; the main buffer switching and high-pressure trigger holding stage maintains the main buffer state after the mechanical push weakens; the main buffer holding and time-limited peak venting stage specifically suppresses the pressure rise at the moment of switching; and the low-pressure trigger reset and adaptive fixed-point replenishment stage suppresses negative pressure and cavitation through local low-pressure trigger replenishment. Thus, it achieves coordinated suppression of pressure spikes, water hammer, end-buffer rigid collisions, rebound, and secondary impacts.

[0045] In a preferred embodiment, the ratio of the equivalent throttling area of ​​the pre-buffered throttling channel 18 to the equivalent throttling area of ​​the main buffered throttling channel 19 can be set to 1.5:1 to 4:1, preferably 2:1 to 3:1; the switching stroke of the sequence valve core 14 from the initial position to the main buffer holding position can be set to 10% to 35% of the total buffer stroke, preferably 15% to 25%; the cone angle of the outer cone push section 32 can be set to 20° to 60°, preferably 30° to 45°; the flow capacity of the reset throttling channel 31 is preferably less than that of the memory charging unidirectional channel 30. The flow capacity is such that the delayed pressure relief required for hydraulic self-holding is achieved; the flow capacity of the rapid pressure relief channel 43 is preferably greater than that of the reset throttling channel 31, so as to quickly release the pressure oil in the pressure memory chamber 29 after the low-pressure trigger reset valve 42 is opened; the opening threshold of the low-pressure trigger reset valve 42 is preferably lower than the pressure level at the end of the pre-buffering and higher than the cavitation initiation pressure; the displacement window corresponding to the peak venting control shoulder 34 is preferably located in the first 20% to 60% range of the main buffer switching stroke of the sequence valve core 14, so that the peak venting action focuses on the pressure rise edge of the initial stage of the main buffer.

[0046] It should be noted that the number, diameter, and axial spacing of the first throttling orifice group 16 and the second throttling orifice group 17, the opening pressure of the memory pressurization one-way channel 30, the diameter of the reset throttling channel 31, the opening threshold of the low-pressure trigger reset valve 42, the diameter of the rapid pressure relief channel 43, the opening threshold of the peak discharge one-way valve 22, the diameter of the replenishment limiting orifice 27, the volume of the replenishment oil storage chamber 36, and the oil supply method of the low-pressure oil source can all be adjusted according to the hydraulic cylinder specifications, the impact load conditions of the marine vertical launch equipment, and the actual vibration reduction requirements. This invention does not limit these aspects.

[0047] The embodiments of the present invention have been described above. However, the embodiments are not limited to the specific implementation methods described above. The specific implementation methods described above are merely illustrative and not restrictive. Those skilled in the art can make more equivalent embodiments under the guidance of the present embodiments, and all of them are within the protection scope of the present embodiments.

Claims

1. A vibration-damping hydraulic cylinder device for offshore vertical launch equipment, characterized in that, It includes a cylinder, a rodless end cap, a piston rod, a piston assembly, a first oil port, a second oil port, a dual threshold sequential buffer assembly, and an adaptive return assembly; the piston assembly is located inside the cylinder and connected to the piston rod, dividing the cylinder into a rodless chamber and a rod chamber, the first oil port is connected to the rodless chamber, and the second oil port is connected to the rod chamber; The dual-threshold sequential buffer assembly includes a buffer plunger, a buffer sleeve, a valve seat, a sequential valve core, a return spring, a pre-buffered throttling channel, a main buffered throttling channel, an annular peak pressure chamber, a peak discharge branch, a pressure memory chamber, a memory pressurization one-way channel, a reset throttling channel, a low-pressure triggered reset valve, and a rapid pressure relief channel; the buffer plunger enters the buffer sleeve at the end of its stroke to form a buffer volume area; The sequence valve core is located inside the valve seat and can move axially relative to the valve seat. An intermediate transition cavity is formed between the outer periphery of the sequence valve core and the inner hole of the valve seat. The sequence valve core is provided with a first throttling orifice group, a second throttling orifice group, a peak discharge control shoulder, and a refill control window. The return spring is used to keep the sequence valve core in its initial position. A local low-pressure sensitive cavity is formed in the local area located on the axial inner side of the flow passage section corresponding to the second throttling orifice group and between the closed end and the flow passage section inside the buffer sleeve. The pressure memory chamber is formed on the side of the sequential valve core away from the buffer plunger. The memory charging one-way channel connects the annular peak pressure chamber and the pressure memory chamber. The reset throttling channel is connected to the pressure memory chamber. The low-pressure trigger reset valve is controlled by the local low-pressure sensitive chamber pressure and causes the pressure memory chamber to be depressurized through the rapid pressure relief channel. The sequential valve core has an inner conical force-bearing section at one end facing the buffer plunger, and an outer conical push section at the end of the buffer plunger that cooperates with it, so that the sequential valve core moves from the initial position to the main buffer position, and is pressurized into the pressure memory chamber through the memory charging one-way channel at the moment of main buffer switching to maintain the main buffer position; When the sequence valve core is in the initial position, the buffer volume area discharges oil through the first throttling orifice group, the intermediate transition chamber, and the pre-buffered throttling channel. When it is in the main buffer position, it discharges oil through the second throttling orifice group, the intermediate transition chamber, and the main buffered throttling channel. The annular peak pressure chamber is connected to the buffer volume area through the radial guide orifice. The peak discharge branch is only opened when the sequence valve core is in the main buffer position and the pressure in the annular peak pressure chamber reaches the threshold, so as to implement time-limited diversion and peak discharge. The sequence valve core has a differential pressure drive end face that is acted upon by the pressure memory chamber. The pressure oil in the pressure memory chamber acts on the differential pressure drive end face to maintain the sequence valve core in the main buffer position after the mechanical push of the buffer plunger is weakened, until the pressure in the local low pressure sensitive chamber drops to a predetermined low pressure threshold and triggers the low pressure trigger reset valve to open. The adaptive replenishment component includes a replenishment reservoir, a replenishment oil circuit, an anti-cavitation check valve, and a replenishment flow restrictor. One end of the replenishment oil circuit is connected to the replenishment reservoir or a low-pressure oil source, and the other end is connected to a local low-pressure sensitive cavity. When the sequence valve core returns to its reset position after the pressure memory cavity is depressurized, it selectively connects the replenishment oil circuit to the local low-pressure sensitive cavity through the replenishment control window.

2. The vibration-damping hydraulic cylinder device for offshore vertical launch equipment according to claim 1, characterized in that, The local low-pressure sensitive cavity is a local cavity located between the inner axial side of the second throttling orifice group and the closed end of the buffer sleeve. During the main buffer switching and rebound depressurization process, the local cavity experiences a pressure drop before the rest of the buffer volume area and serves as the pressure detection source for the low-pressure trigger reset valve.

3. The vibration-damping hydraulic cylinder device for offshore vertical launch equipment according to claim 1, characterized in that, The outer conical push section and the inner conical force-bearing section are mutually cooperating conical surfaces. When the buffer plunger continues to move forward, the outer conical push section and the inner conical force-bearing section form a progressive axial push cooperation, so that the starting displacement and driving force of the sequence valve core gradually increase.

4. A vibration-damping hydraulic cylinder device for offshore vertical launch equipment according to claim 1, characterized in that, The first and second throttling orifice groups are evenly distributed along the circumference of the sequential valve core and spaced apart in the axial direction, and the equivalent throttling area of ​​the pre-buffered throttling channel is greater than the equivalent throttling area of ​​the main buffered throttling channel.

5. A vibration-damping hydraulic cylinder device for offshore vertical launch equipment according to claim 1, characterized in that, The memory pressurization one-way channel allows the pressurized oil in the annular peak pressure chamber to quickly enter the pressure memory chamber and prevents reverse backflow. The flow capacity of the reset throttling channel is less than that of the memory pressurization one-way channel, so that the pressure memory chamber forms a hydraulic self-holding for the sequence valve core. The flow capacity of the rapid pressure relief channel is greater than that of the reset throttling channel, which accelerates the reset of the sequence valve core after the low-pressure trigger reset valve is opened.

6. A vibration-damping hydraulic cylinder device for offshore vertical launch equipment according to claim 1, characterized in that, The intermediate transition chamber selectively connects with the pre-buffered throttling channel, the main buffered throttling channel, the peak discharge branch, and the replenishment oil circuit at different axial positions of the sequential valve core, so that the sequential valve core can complete the pre-buffered, main buffered holding, time-limited peak discharge, and adaptive fixed-point replenishment in sequence within one working cycle.

7. A vibration-damping hydraulic cylinder device for offshore vertical launch equipment according to claim 1, characterized in that, The annular peak pressure chamber is connected to the buffer volume area through multiple radial guide holes arranged circumferentially. The peak release check valve is a spring preloaded check valve. The replenishment oil circuit is connected to the return oil side passage of the first oil port or to the replenishment oil storage chamber, so that at least a portion of the oil diverted through the peak release branch enters the replenishment oil storage chamber.

8. A vibration-damping hydraulic cylinder device for offshore vertical launch equipment according to claim 1, characterized in that, The replenishment flow limiting orifice is located on the replenishment oil line, and the replenishment control window is located on the side of the sequence valve core near the second throttling orifice group. When the sequence valve core is triggered to return to reset via the rapid pressure relief channel, it is aligned and connected with the local low-pressure sensitive chamber.

9. A vibration-damping hydraulic cylinder device for offshore vertical launch equipment according to claim 1, characterized in that, The valve seat is provided with an initial limiting shoulder, a main buffer limiting shoulder, and a refill alignment limiting part to respectively limit the initial position of the sequential valve core, the main buffer holding position, and the alignment connection position of the refill control window.

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