Self-replenishing oil buffer damping hydraulic system for a stowing device

Abstract

The present application relates to a hydraulic cylinder buffer system, in particular to a self-supplying oil buffer damping hydraulic system for a retractable device, comprising a hydraulic control valve block, a buffer control valve group, a skin bag type accumulator and a hydraulic cylinder, the buffer control valve group is arranged between the hydraulic control valve block and the hydraulic cylinder, and the buffer control valve group is connected with the skin bag type accumulator; the buffer control valve group is integrated with a two-position two-way electromagnetic reversing valve A, a throttle valve, a pressure reducing valve and a check valve, a two-position two-way electromagnetic reversing valve B is arranged between the buffer control valve group and the rodless cavity of the hydraulic cylinder, a pressure reducing valve and a check valve are arranged between the buffer control valve group and the skin bag type accumulator, and the pressure reducing valve and the check valve are arranged in parallel. The present application improves the stability and safety of the whole machine, reduces the physical impact of the piston on the hydraulic cylinder, prolongs the service life of the hydraulic cylinder, overcomes the problem that the required oil amount of the hydraulic cylinder is not equal in the buffer state, and has stronger practicality.

Description

Technical Field

[0001] This invention relates to a hydraulic cylinder buffer system, specifically a self-replenishing oil buffer anti-sway hydraulic system for a retraction device. Background Technology

[0002] The deployment and retrieval device for underwater equipment is an important component of the entire underwater operation system. Its function is to complete the deployment and retrieval of underwater equipment under specified sea conditions and water depth.

[0003] During rapid movement, hydraulic cylinders experience strong impacts, noise, and even mechanical collisions at the end of their stroke. This effect is particularly pronounced in high-pressure systems, severely impacting the lifespan of the hydraulic cylinders. Therefore, appropriate braking and cushioning are essential to ensure the longevity of the hydraulic system and cylinders. Currently, the cushioning device in underwater equipment deployment and retrieval systems consists of only a two-position two-way solenoid valve and a throttle valve between the hydraulic cylinder and the control valve block. This hydraulic system design aims to achieve cushioning by controlling the flow of hydraulic oil through the cylinder using these valves. However, with prolonged use and harsh sea conditions, the hydraulic oil gradually flows back to the tank through the superimposed relief valve, reducing the amount of hydraulic oil in the cylinder and significantly weakening the cushioning effect. Furthermore, it fails to address the issue of unequal oil volumes required in the rodless and rod-side chambers during the cushioning process. Summary of the Invention

[0004] The purpose of this invention is to provide a self-replenishing oil buffer anti-sway hydraulic system for a retrieval and deployment device. This system aims to solve the problem that in existing hydraulic cylinder buffer hydraulic systems for underwater equipment retrieval and deployment devices, the hydraulic cylinder experiences a reaction force due to physical impact, affecting its service life. It also addresses the issue that the hydraulic cylinder buffer system cannot recover energy during retrieval and deployment operations, and resolves the problem of unequal oil volume required in the rodless and rod-side chambers of the hydraulic cylinder under buffer mode.

[0005] The objective of this invention is achieved through the following technical solution:

[0006] This invention includes a hydraulic control valve block, a buffer control valve assembly, a bladder accumulator, and a hydraulic cylinder. A buffer control valve assembly is provided between the hydraulic control valve block and the hydraulic cylinder, and the buffer control valve assembly is connected to the bladder accumulator. The buffer control valve assembly integrates a two-position two-way solenoid directional valve A, a throttle valve, a pressure reducing valve, and a check valve. A two-position two-way solenoid directional valve B is provided between the buffer control valve assembly and the rodless chamber of the hydraulic cylinder. A pressure reducing valve and a check valve are provided between the buffer control valve assembly and the bladder accumulator, and the pressure reducing valve and the check valve are arranged in parallel.

[0007] Wherein: a safety and shut-off valve block is provided between the buffer control valve group and the bladder accumulator.

[0008] The PY port of the buffer control valve group is connected to the oil tank. The PW port of the buffer control valve group is connected to the rodless chamber of the hydraulic cylinder and the hydraulic control valve block via the two-position two-way solenoid directional valve B. The L port of the buffer control valve group is connected to the oil tank.

[0009] The PY port of the buffer control valve group flows through the two-position two-way solenoid directional valve A, the throttle valve, the pressure reducing valve, and is connected to the PX port of the buffer control valve group. The PX port of the buffer control valve group is connected to the bladder accumulator. The oil inlet of the check valve is connected to the oil outlet of the pressure reducing valve. The oil outlet of the check valve is connected to the oil inlet of the pressure reducing valve. The oil inlet of the pressure reducing valve is also connected to the PW port of the buffer control valve group. The overflow port of the pressure reducing valve is connected to the L port of the buffer control valve group.

[0010] The hydraulic control valve block sequentially comprises a stacked relief valve, a stacked pilot-operated check valve, and a three-position four-way solenoid directional valve. The P1 port of the hydraulic control valve block is connected to the P ports of the three-position four-way solenoid directional valve, the stacked pilot-operated check valve, and the stacked relief valve. The T1 port of the hydraulic control valve block is connected to the T ports of the three-position four-way solenoid directional valve, the stacked pilot-operated check valve, and the stacked relief valve. The A1 port of the hydraulic control valve block is connected to the A port of the three-position four-way solenoid directional valve and the stacked pilot-operated check valve. Port A of the hydraulic control valve block is connected to Port A of the stacked relief valve. Port B1 of the hydraulic control valve block is connected to Port B of the three-position four-way solenoid directional valve, Port B of the stacked hydraulic control check valve, and Port B of the stacked relief valve. Port P1 of the hydraulic control valve block is connected to the oil pump. Port T1 of the hydraulic control valve block is connected to the oil tank. Port A1 of the hydraulic control valve block is connected to the buffer control valve group and the rod chamber of the hydraulic cylinder. Port B1 of the hydraulic control valve block is connected to the oil outlet of the two-position two-way solenoid directional valve B and the rodless chamber of the hydraulic cylinder.

[0011] The advantages and positive effects of this invention are as follows:

[0012] 1. This invention improves the overall stability of the machine, reduces the physical impact of the piston on the hydraulic cylinder, and extends the service life of the hydraulic cylinder.

[0013] 2. During the launching and retracting operation, the present invention generates a corresponding buffering effect on the hydraulic cylinder through the hydraulic damping effect of the throttle valve in the circuit.

[0014] 3. The present invention incorporates a bladder-type accumulator in the circuit, which can recover hydraulic energy during the deployment and retraction operation.

[0015] 4. In the buffer mode, the present invention provides an oil collection and replenishment device in the circuit to overcome the problem that the required oil volume is different between the rodless chamber and the rod chamber of the hydraulic cylinder.

[0016] 5. This invention improves the overall safety of the underwater operation equipment deployment and retrieval device and enhances its practicality. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of the present invention;

[0018] Wherein: 1 is an oil pump, 2 is a three-position four-way solenoid directional valve, 3 is a stacked hydraulic control check valve, 4 is a stacked relief valve, 5 is a hydraulic control valve block, 6 is a buffer control valve group, 7 is a two-position two-way solenoid directional valve A, 8 is a throttle valve, 9 is a pressure reducing valve, 10 is a check valve, 11 is a safety and shut-off valve block, 12 is a bladder accumulator, 13 is a hydraulic cylinder A, 14 is a two-position two-way solenoid directional valve B, 15 is an oil tank, and 16 is a hydraulic cylinder B. Detailed Implementation

[0019] The invention will now be described in further detail with reference to the accompanying drawings.

[0020] like Figure 1 As shown, the present invention includes a hydraulic control valve block 5, a buffer control valve assembly 6, a bladder accumulator 12, and a hydraulic cylinder. The buffer control valve assembly 6 is provided between the hydraulic control valve block 5 and the hydraulic cylinder, and the buffer control valve assembly 6 is connected to the bladder accumulator 12. The buffer control valve assembly 6 integrates a two-position two-way solenoid directional valve A7, a throttle valve 8, a pressure reducing valve 9, and a check valve 10. A two-position two-way solenoid directional valve B14 is provided between the buffer control valve assembly 6 and the rodless chamber of the hydraulic cylinder. A pressure reducing valve 9 and a check valve 10 are provided between the buffer control valve assembly 6 and the bladder accumulator 12. The pressure reducing valve 9 and the check valve 10 are arranged in parallel.

[0021] In this embodiment, there are two hydraulic cylinders, namely hydraulic cylinder A13 and hydraulic cylinder B16.

[0022] In this embodiment, a safety and shut-off valve block 11 is provided between the buffer control valve group 6 and the bladder accumulator 12. The safety and shut-off valve block 11 in this embodiment is prior art and will not be described in detail here.

[0023] In this embodiment, the PY port of the buffer control valve group 6 flows through the two-position two-way solenoid directional valve A7, the throttle valve 8, and the pressure reducing valve 9, and is connected to the PX port of the buffer control valve group 6. The PX port of the buffer control valve group 6 is connected through the safety and shut-off valve block 11 and the bladder accumulator 12. The PY port of the buffer control valve group 6 is connected to the A1 port of the hydraulic control valve block 5. The oil inlet of the check valve 10 is connected to the oil outlet of the pressure reducing valve 9, and the oil outlet of the check valve 10 is connected to the oil inlet of the pressure reducing valve 9. The oil inlet of the pressure reducing valve 9 is also connected to the PW port of the buffer control valve group 6. The PW port of the buffer control valve group 6 is connected through the two-position two-way solenoid directional valve B14 and then to the rodless chamber of the hydraulic cylinder A13, the hydraulic cylinder B16, and the hydraulic control valve block 5, respectively. The overflow port of the pressure reducing valve 9 is connected to the L port of the buffer control valve group 6, and the L port of the buffer control valve group 6 is connected to the oil tank 15.

[0024] In this embodiment, the hydraulic control valve block 5 is sequentially stacked with a stacked relief valve 4, a stacked hydraulic control check valve 3, and a three-position four-way solenoid directional valve 2. The P1 port of the hydraulic control valve block 5 is connected to the P ports of the three-position four-way solenoid directional valve 2, the stacked hydraulic control check valve 3, and the stacked relief valve 4. The T1 port of the hydraulic control valve block 5 is connected to the T ports of the three-position four-way solenoid directional valve 2, the stacked hydraulic control check valve 3, and the stacked relief valve 4. The A1 port of the hydraulic control valve block 5 is connected to the three-position four-way solenoid directional valve... Port A of valve 2, port A of stacked hydraulic control check valve 3, and port A of stacked relief valve 4 are connected. Port B1 of hydraulic control valve block 5 is connected to port B of three-position four-way solenoid directional valve 2, port B of stacked hydraulic control check valve 3, and port B of stacked relief valve 4. Port P1 of hydraulic control valve block 5 is connected to oil pump 1. Port T1 of hydraulic control valve block 5 is connected to oil tank 15. Port A1 of hydraulic control valve block 5 is connected to port PY of buffer control valve group 6. Port B1 of hydraulic control valve block 5 is connected to port PW of buffer control valve group 6.

[0025] The oil pump 1 and oil tank 15 of the present invention can be the oil pump and oil tank in the hydraulic system of the retraction device.

[0026] The working principle of this invention is as follows:

[0027] When in the retraction / extension operation mode, the swing frame swings outward, and hydraulic cylinders A13 and B16 extend actively. The solenoid D2 of the three-position four-way solenoid valve 2 and the solenoid D4 of the two-position two-way solenoid valve B14 are energized, while the solenoid D3 of the two-position two-way solenoid valve A7 is de-energized. The three-position four-way solenoid valve 2 is in the right position, the two-position two-way solenoid valve B14 is connected, and the two-position two-way solenoid valve A7 is disconnected. The oil pump 1 pumps the hydraulic oil from the oil tank 15. A portion of the pressurized hydraulic oil flows into the rodless chambers of hydraulic cylinders A13 and B16, causing the piston rods of hydraulic cylinders A13 and B16 to extend. Another portion of the pressurized hydraulic oil flows through the two-position two-way solenoid valve B14 and into the PW port of the buffer control valve group 6. The hydraulic oil flowing into the PW port of the buffer control valve group 6 is then used by the pressure reducing valve 9 to fill the bladder accumulator 12.

[0028] When in the retraction / extension operation mode, as the swing frame swings inward and hydraulic cylinders A13 and B16 retract actively, the solenoid D1 of the three-position four-way solenoid valve 2 and the solenoid D4 of the two-position two-way solenoid valve B14 are energized, while the solenoid D3 of the two-position two-way solenoid valve 7 is de-energized. The three-position four-way solenoid valve 2 is in the left position, the two-position two-way solenoid valve B14 is connected, and the two-position two-way solenoid valve A7 is disconnected. Oil pump 1 pumps hydraulic oil from oil tank 15, pressurizing the hydraulic oil. The piston rods of hydraulic cylinders A13 and B16 begin to retract, and the rodless chambers of hydraulic cylinders A13 and B16 begin to discharge oil. The hydraulic oil flowing out of the rodless chambers of hydraulic cylinders A13 and B16 passes through the two-position two-way solenoid valve B14 and flows into the PW port of the buffer control valve group 6. The hydraulic oil flowing into the PW port of the buffer control valve group 6 is then used to fill the bladder accumulator 12 by the pressure reducing valve 9.

[0029] When in buffer mode, the solenoid D3 of the 2-position 2-way solenoid directional valve A7 and the solenoid D4 of the 2-position 2-way solenoid directional valve B14 are energized, and the 3-position 4-way solenoid directional valve 2 is in the neutral position. When the waves recede, the piston rods of hydraulic cylinders A13 and B16 extend, and hydraulic oil flows out from the rod chambers of hydraulic cylinders A13 and B16. Part of the hydraulic oil flowing out from the rod chambers of hydraulic cylinders A13 and B16 flows into the buffer control valve group 6 through the PY port and then through the 2-position 2-way solenoid directional valve A7, the throttle valve 8, and the 2-position 4-way solenoid directional valve B14. The hydraulic oil flows back to the rodless chambers of hydraulic cylinders A13 and B16 via the two-way solenoid directional valve B14; another portion of the hydraulic oil flows directly back to the oil tank 15 through the T1 port of the hydraulic control valve block 5; the hydraulic oil discharged from the bladder accumulator 12 flows into the buffer control valve group 6 through the PX port and then through the check valve 10, where it merges with the hydraulic oil flowing out of the rod chambers of hydraulic cylinders A13 and B16, flows out from the PW port of the buffer control valve group 6, and flows back to the rodless chambers of hydraulic cylinders A13 and B16 via the two-position two-way solenoid directional valve B14.

[0030] When in buffer mode, the solenoid D3 of the two-position two-way solenoid directional valve A7 and the solenoid D4 of the two-position two-way solenoid directional valve B14 are energized, and the three-position four-way solenoid directional valve 2 is in the neutral position. When the waves rise, the piston rods of hydraulic cylinders A13 and B16 are retracted, and hydraulic oil flows out from the rodless chambers of hydraulic cylinders A13 and B16. The hydraulic oil flowing out from the rodless chambers of hydraulic cylinders A13 and B16 flows through the two-position two-way solenoid valve B14 and into the PW port of the buffer control valve group 6. Part of the hydraulic oil flowing into the PW port of the buffer control valve group 6 is charged to the bladder accumulator 12 by the pressure reducing valve 9, and the other part of the hydraulic oil flows out of the PY port of the buffer control valve group 6 through the throttle valve 8 and the two-position two-way solenoid directional valve A7 and flows back to the rod chambers of hydraulic cylinders A13 and B16.

Claims

1. A self-replenishing oil-buffered anti-sway hydraulic system for a retraction device, characterized in that: The system includes a hydraulic control valve block (5), a buffer control valve group (6), a bladder accumulator (12), and a hydraulic cylinder. The buffer control valve group (6) is provided between the hydraulic control valve block (5) and the hydraulic cylinder, and the buffer control valve group (6) is connected to the bladder accumulator (12). The buffer control valve group (6) integrates a two-position two-way solenoid directional valve A (7), a throttle valve (8), a pressure reducing valve (9), and a check valve (10). A two-position two-way solenoid directional valve B (14) is provided between the buffer control valve group (6) and the rodless chamber of the hydraulic cylinder. A pressure reducing valve (9) and a check valve (10) are provided between the buffer control valve group (6) and the bladder accumulator (12). The pressure reducing valve (9) and the check valve (10) are connected in parallel.

2. The self-replenishing oil buffer anti-sway hydraulic system for the retraction device according to claim 1, characterized in that: A safety and shut-off valve block (11) is provided between the buffer control valve group (6) and the bladder accumulator (12).

3. The self-replenishing oil buffer anti-sway hydraulic system for the retraction device according to claim 1, characterized in that: The PY port of the buffer control valve group (6) is connected to the oil tank (15). The PW port of the buffer control valve group (6) is connected to the rodless chamber of the hydraulic cylinder and the hydraulic control valve block (5) respectively through the two-position two-way solenoid directional valve B (14). The L port of the buffer control valve group (6) is connected to the oil tank (15).

4. The self-replenishing oil buffer anti-sway hydraulic system for the retraction device according to claim 1, characterized in that: The PY port of the buffer control valve group (6) flows through the two-position two-way solenoid directional valve A (7), the throttle valve (8), and the pressure reducing valve (9) and is connected to the PX port of the buffer control valve group (6). The PX port of the buffer control valve group (6) is connected to the bladder accumulator (12). The oil inlet of the check valve (10) is connected to the oil outlet of the pressure reducing valve (9). The oil outlet of the check valve (10) is connected to the oil inlet of the pressure reducing valve (9). The oil inlet of the pressure reducing valve (9) is also connected to the PW port of the buffer control valve group (6). The overflow port of the pressure reducing valve (9) is connected to the L port of the buffer control valve group (6).

5. The self-replenishing oil buffer anti-sway hydraulic system for the retraction device according to claim 1, characterized in that: The hydraulic control valve block (5) is composed of a stacked relief valve (4), a stacked hydraulic control check valve (3), and a three-position four-way solenoid directional valve (2) stacked sequentially. The P1 port of the hydraulic control valve block (5) is connected to the P port of the three-position four-way solenoid directional valve (2), the P port of the stacked hydraulic control check valve (3), and the P port of the stacked relief valve (4). The T1 port of the hydraulic control valve block (5) is connected to the T port of the three-position four-way solenoid directional valve (2), the stacked hydraulic control check valve (3), and the P port of the stacked hydraulic control check valve (4). The T port of the check valve (3) and the T port of the stacked relief valve (4) are connected. The A1 port of the hydraulic control valve block (5) is connected to the A port of the three-position four-way solenoid directional valve (2), the A port of the stacked hydraulic control check valve (3), and the A port of the stacked relief valve (4). The B1 port of the hydraulic control valve block (5) is connected to the B port of the three-position four-way solenoid directional valve (2), the B port of the stacked hydraulic control check valve (3), and the B port of the stacked relief valve (4). The P1 port of the hydraulic control valve block (5) is connected to the oil pump (1), the T1 port of the hydraulic control valve block (5) is connected to the oil tank (15), the A1 port of the hydraulic control valve block (5) is connected to the buffer control valve group (6) and the rod chamber of the hydraulic cylinder respectively, and the B1 port of the hydraulic control valve block (5) is connected to the oil outlet of the two-position two-way solenoid directional valve B (14) and the rodless chamber of the hydraulic cylinder respectively.

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