CN111503067A - Acceleration pressurization system - Google Patents

Abstract

The invention discloses an acceleration and supercharging system, comprising a second switching valve, a double-acting oil cylinder and a third switching valve arranged on the inlet and outlet oil passages of an execution oil cylinder; the inside of the double-acting oil cylinder is a piston with a large end and a small end, The large end and the small end of the corresponding piston are respectively the large cavity and the small cavity of the double-acting oil cylinder. The switching valve is arranged on the branch connected to the large cavity of the double-acting oil cylinder; the third switching valve is arranged on the working oil return road of the execution oil cylinder, and the oil return port of the execution oil cylinder is between the working oil return circuit and the working oil inlet circuit. Toggle connections. On the premise that the displacement and pressure level of the main pump do not need to be changed, the present invention can accelerate the no-load running speed of the execution oil cylinder by adding the acceleration boosting system of the present invention to the working oil circuit of the execution oil cylinder, and increase the maximum output force of the oil cylinder load. Realize the rapid or large thrust extension of the execution cylinder.

Description

Acceleration boost system

technical field

The invention belongs to the hydraulic control technology, and particularly relates to an acceleration boosting system of a hydraulic oil cylinder.

Background technique

In the construction machinery, construction machinery and factory automation equipment using hydraulic drive, the hydraulic cylinder is the main actuator. Due to the actual work requirements and lightweight design considerations, the hydraulic cylinder requires the speed to move to the contact load during the no-load process, and it is necessary to increase the flow rate. , After the load, the pressure needs to be increased to perform work on the load. The flow and pressure required by the hydraulic cylinder are often inconsistent. Therefore, there is a situation where a single or a few groups of actions need to output a large thrust and use a large-bore high-pressure cylinder.

The current solution is to select the corresponding pressure level of the hydraulic system and the displacement of the main pump according to the requirements of the large-bore high-pressure cylinder to meet the high-pressure and large-flow output of the hydraulic cylinder, and then set the secondary overflow and speed regulation in the hydraulic system to achieve The low pressure and small flow output of the hydraulic cylinder, so the corresponding components in the hydraulic system must be selected according to the large flow and high pressure, resulting in high cost.

SUMMARY OF THE INVENTION

The technical problem solved by the present invention is: to provide an accelerated pressurization system, which can realize the accelerated extension and high pressure driving of the hydraulic cylinder without changing the flow rate and pressure level of the existing hydraulic system, and effectively control the cost of the hydraulic system of the equipment.

The present invention adopts the following technical scheme to realize:

The acceleration boosting system includes a second switching valve 5, a double-acting cylinder 6 and a third switching valve 8 arranged on the inlet and outlet oil passages of the execution cylinder;

The inside of the double-acting oil cylinder 6 is a piston with a large end and a small end, and the large and small ends of the corresponding piston are respectively the large cavity and the small cavity of the double-acting oil cylinder. The second switching valve 5 is arranged on the branch connected to the large cavity of the double-acting oil cylinder 6;

The third switching valve 8 is arranged on the working oil return line of the execution oil cylinder, and switches and connects the oil return port of the execution oil cylinder between the working oil return line and the working oil inlet line.

Further, an accumulator 1 is also included, the accumulator 1 is connected and arranged on the working oil inlet of the execution oil cylinder through a branch circuit, and the branch circuit of the accumulator 1 is provided with a first switching valve 2 .

Further, the first switching valve 2 is a two-position two-way reversing valve, including a communication position and a cut-off position.

Further, a hydraulically controlled check valve 7 connected in parallel with the double-acting oil cylinder 6 is also provided on the working oil inlet of the execution cylinder, and the pilot oil circuit of the hydraulically controlled check valve 7 is connected with the working oil return circuit of the execution cylinder. .

Further, the second switching valve 5 is a two-position three-way reversing valve, including a communication position and a cut-off position, and at the cut-off position, there is an intercommunication connecting the big end of the double-acting oil cylinder 6 at both ends of the large cavity. oil road.

Further, the large cavity of the double-acting oil cylinder 6 is connected to the working oil return line through the oil drain line on the side close to the small end.

Further, the third switching valve 8 is a two-position three-way reversing valve, including an oil return working position and a confluence working position, and the oil return working position communicates the oil return port of the execution cylinder with the working oil return circuit, so The confluence working position communicates the oil return port of the execution cylinder with the working oil inlet.

Further, a first check valve 3 and a second check valve 4 are respectively provided on the parallel sections of the working oil inlet road corresponding to the hydraulic control check valve 7 and the double-acting oil cylinder 6 .

As a preferred solution of the acceleration and supercharging system of the present invention, the first switching valve 2 , the second switching valve 5 and the third switching valve 8 are hydraulically controlled switching valves, and the first switching valve 2 and the third switching valve 8 The switching valves 8 are all switched by pilot pressure oil, and the second switching valve 5 is connected to the small cavity of the double-acting oil cylinder 6 through a pilot oil circuit.

As another preferred solution of the acceleration and supercharging system of the present invention, the first switching valve 2 , the second switching valve 5 and the third switching valve 8 are electronically controlled directional valves.

In the acceleration boosting system of the present invention, when the execution oil cylinder is unloaded and extended, the pumped pressure oil enters the working oil inlet circuit of the execution oil cylinder, and the hydraulic oil stored in the accumulator merges into the working oil inlet passage through the first switching valve. The return oil of the execution oil cylinder joins into the working oil inlet circuit through the third switching valve, which increases the amount of oil entering the execution oil cylinder. The confluent hydraulic oil enters the oil cylinder through the first check valve and the second check valve in the working oil inlet passage. The large cavity allows the actuator cylinder to extend quickly.

When the load of the execution cylinder is extended, the pumped pressure oil enters the working oil inlet of the execution cylinder. Due to the increase of the back pressure in the working oil inlet pipe, a part of the pressure oil enters the accumulator through the first switching valve for storage, and a part is stored in the accumulator through the first switching valve. The second switching valve is pressurized by the double-acting oil cylinder and then enters the execution oil cylinder to realize the supercharging of the execution oil cylinder.

When the execution oil cylinder is retracted, the pumped pressure oil enters the working oil return circuit of the execution oil cylinder, and enters the execution oil cylinder through the third switching valve to drive the oil cylinder to retract. The return oil of the oil cylinder is returned to the oil tank through the hydraulic control check valve and the working oil inlet circuit.

The beneficial effects of the present invention are: without changing the displacement and pressure level of the main pump, by adding the acceleration boosting system of the present invention to the working oil circuit of the execution oil cylinder, the no-load running speed of the execution oil cylinder can be accelerated, and the load of the oil cylinder can be increased. The maximum output force can be automatically identified and switched in the whole process according to the change of system pressure caused by the load of the execution cylinder. The entire system is a common hydraulic component, which is easy to install and costs less than large parts such as high-power main pumps.

The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

Description of drawings

FIG. 1 is a hydraulic schematic diagram of the acceleration and boosting system in the first embodiment.

FIG. 2 is a schematic diagram of the hydraulic principle of the acceleration and booster system in the first embodiment when the execution oil cylinder is in a no-load extension state.

FIG. 3 is a schematic diagram of the hydraulic principle of the acceleration and booster system in the first embodiment when the execution oil cylinder is in a load extension state.

FIG. 4 is a schematic diagram of the hydraulic principle of the acceleration and booster system in the first embodiment when the execution oil cylinder is in a retracted state.

FIG. 5 is a hydraulic schematic diagram of the acceleration and boosting system in the second embodiment.

Labels in the figure: 1-accumulator, 2-first switching valve, 3-first one-way valve, 4-second one-way valve, 5-second switching valve, 6-double-acting oil cylinder, 7-hydraulic control Check valve, 8-the third switching valve, 9-actuating oil cylinder, 100-working oil inlet circuit, 200-working oil return circuit.

Detailed ways

Example 1

Referring to FIG. 1 , the acceleration boosting system shown in the figure is a specific embodiment of the present invention, which specifically includes an accumulator 1 , a first switching valve 2 , a first one-way valve 3 , a second one-way valve 4 , a first The second switching valve 5 , the double-acting oil cylinder 6 , the hydraulic control one-way valve 7 and the third switching valve 8 . With reference to FIGS. 2 and 3 , the acceleration and boosting system of this embodiment achieves the purpose of no-load acceleration and load boosting in the process of performing the work of the oil cylinder 9 . The acceleration and supercharging system of this embodiment is arranged on the oil inlet and outlet of the execution cylinder 9, wherein the large cavity and the small cavity of the execution cylinder 9 are respectively connected to the A1 port and the B1 port of the acceleration supercharging system, and the A port of the acceleration supercharging system is connected. Port and port B are respectively connected to the working oil port of the reversing valve of the hydraulic system of the execution oil cylinder 9, and the reversing control oil circuit of the hydraulic oil cylinder belongs to the conventional technology, and is not repeated here in this embodiment.

In this embodiment, the piston of the execution oil cylinder 9 is extended outward as the work state, and the working oil inlet 100 refers to the pressure oil path in which the pumped hydraulic oil enters the large cavity of the execution oil cylinder 9 and pushes the piston to extend outward to do work. The working oil return circuit 200 refers to an oil return oil circuit through which the return oil in the small cavity of the oil cylinder returns to the oil tank when the execution oil cylinder is extended outward to do work. In practical applications, the connection sequence of the designed working oil circuit and working oil return circuit and the large cavity and small cavity of the execution cylinder can be adjusted according to the specific working conditions.

Specifically, the acceleration boosting system of this embodiment uses the accumulator 1 and the return oil confluence of the execution cylinder to increase the hydraulic oil flow into the execution cylinder, and increases the extension speed of the execution cylinder 9. The pressure action increases the hydraulic oil pressure entering the execution cylinder and increases the extension pressure of the execution cylinder 9 .

The inside of the double-acting oil cylinder 6 is a piston with a large end and a small end, that is, the piston has two piston heads, a large end with a larger area and a small end with a small area, and the large and small ends of the corresponding piston are respectively double-acting oil cylinders The large cavity and the small cavity of 6, the large cavity and the small cavity of the double-acting oil cylinder 6 are respectively connected to the working oil inlet 100 of the execution oil cylinder 9 through the branch circuit, and the double-acting oil cylinder 6 and the working oil inlet 100 of the executive oil cylinder 9 are connected. Arranged in parallel, the second switching valve 5 is arranged on the branch connected with the large cavity of the double-acting oil cylinder 6, the branch between the small cavity of the double-acting oil cylinder 6 and the working oil inlet 100 is normally connected, and the second switching valve 5 is two. The three-way reversing valve includes a communication position and a cut-off position, wherein the communication position connects the large cavity of the double-acting oil cylinder 6 with the working oil inlet 100, and the cut-off position cuts off the large cavity of the double-acting oil cylinder 6 and the working oil inlet 100. At the cut-off position of the second switching valve 5, there is an interconnecting oil circuit connecting the large end of the double-acting oil cylinder 6 at both ends of the large cavity, and the large cavity of the double-acting oil cylinder 6 is connected on the side close to the small end through the oil drain circuit To the working oil return circuit 200, in this way, whether the second switching valve 5 is in the connecting position or the blocking position, the big end piston of the double-acting oil cylinder 6 moves normally inside the large cavity.

The third switching valve 8 is arranged on the working oil return path 200 of the execution oil cylinder 9, and switches the oil return port of the execution oil cylinder 9 between the working oil return path 200 and the working oil inlet path 100. The third switching valve 8 is two The three-way reversing valve includes the oil return working position and the confluence working position. The oil return working position connects the oil return port of the execution cylinder 9 with the working oil return circuit 200, so that the return oil of the execution cylinder 9 can be directly returned to the oil tank, and the confluence work is realized. The oil return port of the execution oil cylinder 9 is communicated with the working oil inlet passage 100, so that the return oil and the oil inlet of the execution oil cylinder 9 are merged and the working speed of the execution oil cylinder is improved.

The accumulator 1 is connected and arranged on the working oil inlet 100 of the execution cylinder 9 through a branch circuit, the first switching valve 2 is arranged on the connecting branch between the working oil inlet 100 and the accumulator 1, and the first switching valve 2 is two. The two-way reversing valve includes a communication position and a cut-off position, wherein the communication position connects the accumulator 1 and the working oil inlet 100, and the cut-off position cuts off the connection between the accumulator 1 and the working oil inlet 100.

In addition, a hydraulic control check valve 7 connected in parallel with the double-acting oil cylinder 6 is also provided on the working oil inlet of the execution oil cylinder 9, and the pilot oil circuit of the hydraulic control check valve 7 is connected with the working oil return circuit of the execution oil cylinder. When the actuator cylinder 9 is in the retracted state, it serves as the oil return route of the working oil inlet passage 100 . The first check valve 3 and the second check valve 4 are respectively provided on the parallel sections of the hydraulic control check valve 7 and the double-acting oil cylinder 6 on the working oil inlet. The check valve ensures the normal operation of each parallel hydraulic component.

In this embodiment, the first switching valve 2, the second switching valve 5 and the third switching valve 8 are hydraulically controlled switching valves, and the first switching valve 2 and the third switching valve 8 are all switched by pilot pressure oil, that is, The pressure oil passing through the first switching valve 2 and the third switching valve 8 will be partially connected to the pilot hole of the corresponding switching valve, pushing the spool to switch the direction, and the second switching valve 5 will be connected to the double-acting oil cylinder through the pilot oil circuit The small cavity of 6 uses the pressure built up after the piston in the double-acting oil cylinder is in place to push the second reversing valve 5 for reversing switching.

The working principle of the acceleration and supercharging system of this embodiment will be described in detail below.

When the oil cylinder is inactive, the valve cores of the first switching valve 2, the second switching valve 5, and the third switching valve 8 stop at the initial position under the action of the spring force, and the accumulator 1 stores part of the pressure oil.

As shown in Figure 2, when the execution cylinder 9 is extended without load, the pumped pressure oil is fed from port A to the working oil inlet 100, the first switching valve 2 is switched to the upper position under the action of pressure, and the accumulator 1 The pressure oil stored in the first switching valve 2 is released through the upper position of the first switching valve 2 and merges with the inlet oil in the working oil inlet circuit 100; at the same time, the pressure is not enough to push the third switching valve 8, and the third switching valve 8 is maintained in the right position; when the working oil inlet After the pressure oil in the passage 100 enters the large cavity of the execution cylinder 9, the return oil from the small cavity of the execution cylinder 9 merges with the oil inlet of the working oil inlet passage 100 through the right position of the third switching valve 8. The pressure of the second switching valve 5 is balanced and maintained in the lower position, and the double-acting oil cylinder 6 does not act. In the working state of FIG. 2 , the pumped pressure oil, the pressure oil released by the accumulator 1 and the small cavity return oil of the actuator cylinder 9 merge in the working oil inlet 100 and pass through the first check valve 3 and the second check valve 3 . The direction valve 4 and the hydraulic control check valve 7 enter the large cavity of the actuator cylinder 9 to realize the accelerated extension of the piston rod of the actuator cylinder 9 .

As shown in Figure 3, when the actuator cylinder 9 is extended with a load, the inlet oil pressure of port A increases, the first switching valve 2 is switched to the upper position under the action of the pressure, and part of the pressure oil enters the lower position through the first switching valve 2 At the same time, the third switching valve 8 is switched to the left position under the action of the pressure oil, and the small cavity of the execution cylinder 9 is directly connected to the fuel tank through the left position of the third switching valve 8. In the working oil inlet 100, the pressure oil enters the small cavity of the double-acting oil cylinder 6 through the first check valve 3, and the piston rod in the double-acting oil cylinder 6 runs to the large cavity until the small cavity is filled with pressure oil, and the double-acting oil cylinder 6 The internal return oil is returned to the oil tank through the third switching valve 8 in the left position through the oil drain path. As the pressure of the small cavity of the double-acting oil cylinder 6 increases, the spool of the second switching valve 5 is pushed to switch to the upper position, and the working oil path is switched to the upper position. 100 is connected with the large cavity of the double-acting oil cylinder 6, and the pressure oil of the working oil inlet 100 enters the large cavity of the double-acting oil cylinder 6 through the upper position of the second switching valve 5, and pushes the piston rod of the double-acting oil cylinder 6 to move to the small cavity. The return oil of 6 returns to the oil tank through the oil drain path through the third switching valve 8 at the left position. Due to the area difference between the large cavity and the small cavity of the double-acting cylinder 6, when the double-acting cylinder 6 piston rod moves from the large cavity to the small cavity When the hydraulic oil in the small cavity of the double-acting oil cylinder 6 is pressurized, it enters the large cavity of the execution oil cylinder 9 through the second one-way valve 4, and the piston rod of the execution oil cylinder 9 is pressurized and extended. When the piston rod of the double-acting oil cylinder 6 runs to the top of the small cavity and the large cavity is full, the small cavity of the double-acting oil cylinder 6 is cut off from the pilot pressure oil of the second switching valve 5, and the second switching valve 5 is reset and switched to the lower position, working The pressure oil of the oil inlet 100 fills the small cavity of the double-acting oil cylinder 6 with liquid again, and through the repeated switching of the second switching valve 5 and the reciprocating motion of the double-acting oil cylinder 6, the execution oil cylinder 9 realizes the pressurization action during the continuous extension process. .

As shown in Figure 4, when the execution oil cylinder 9 is retracted after completing the extension action, the hydraulic system reversing valve switches the working oil inlet circuit and the working oil return circuit. 200 is the oil inlet, the pumped pressure oil enters the oil from the B port, the third switching valve 8 is switched to the left position under the action of the pressure, and the hydraulic control check valve 7 is opened under the action of the oil inlet pressure, and the pressure oil starts to work. The oil return line 200 enters the small cavity of the actuator cylinder 9 through the left position of the third switching valve 8, pushes the piston rod of the actuator cylinder 9 to retract, and the oil return from the large cavity of the actuator cylinder 9 passes through the bypass where the hydraulic control check valve 7 is located. The oil circuit returns oil from port A, and the first check valve 3 and the second check valve 4 arranged on the working oil inlet circuit 100 prevent the return oil from entering the double-acting oil cylinder 6 .

Embodiment 2

Referring to FIG. 5 , this embodiment is another specific implementation of the acceleration and supercharging system of the present invention, and the difference from the first embodiment is that the first switching valve 2 , the second switching valve 5 and the first switching valve 5 in this embodiment are different from the first embodiment. The three switching valves 8 are all electrically controlled reversing valves, and the electrically controlled reversing valves can be triggered and switched by a pressure sensor or a position sensor arranged on the oil circuit.

For example, both the first switching valve 2 and the third switching valve 8 are feedback controlled by a pressure sensor arranged on the working oil inlet 100 , and the action of the second switching valve 5 is fed back according to a position sensor that detects the movement of the piston of the double-acting oil cylinder 6 . control.

When the execution cylinder 9 is extended without load, the pumped pressure oil is fed from port A to the working oil inlet 100. As long as the pressure build up inside the working oil passage 100 is detected, the first switching valve 2 can be controlled to switch to the working oil inlet 100. In the upper position, the pressure oil stored in the accumulator 1 is released through the upper position of the first switching valve 2 and merges with the inlet oil in the working oil inlet 100; because it is no-load, the oil inlet pressure in the working oil inlet 100 at this time does not reach 100. The pressure threshold value of the switching of the third switching valve 8, the third switching valve 8 is maintained in the right position; the second switching valve 5 is maintained in the lower position according to the detected piston position of the double-acting cylinder 6, the double-acting cylinder 6 does not act, and the pumping The pressure oil, the pressure oil released by the accumulator 1 and the small cavity return oil of the actuator cylinder 9 merge in the working oil inlet 100 and enter through the first check valve 3, the second check valve 4 and the hydraulic control check valve 7. The large cavity of the execution oil cylinder 9 realizes the accelerated extension of the piston rod of the execution oil cylinder 9.

When the actuator cylinder 9 is extended with a load, the inlet oil pressure of port A increases, the first switching valve 2 is still switched to the upper position, and part of the pressure oil enters the accumulator through the lower position of the first switching valve 2 to store energy; this When the internal back pressure of the working oil inlet 100 increases due to the load, the pressure signal reaches the switching threshold of the third switching valve 8 and switches to the left position. The small cavity of the execution cylinder 9 is directly connected to the fuel tank through the left position of the third switching valve 8. In the working oil inlet 100, the pressure oil enters the small cavity of the double-acting oil cylinder 6 through the first check valve 3, and the piston rod in the double-acting oil cylinder 6 runs to the large cavity until the small cavity is filled with pressure oil, and the double-acting oil cylinder 6 The internal return oil returns to the oil tank through the third switching valve 8 in the left position through the oil drain path. As the piston of the double-acting oil cylinder 6 moves to the limit position of the large cavity, the detected piston position signal triggers the control of the second switching valve 5. The valve core is switched to the upper position, connecting the working oil passage 100 with the large cavity of the double-acting cylinder 6, and the pressure oil of the working oil passage 100 enters the large cavity of the double-acting cylinder 6 through the upper position of the second switching valve 5, and pushes the double-acting cylinder. 6. The piston rod moves to the small cavity, and the return oil of the double-acting oil cylinder 6 returns to the oil tank through the third switching valve 8 in the left position through the oil drain path. Due to the area difference between the large cavity and the small cavity of the double-acting oil When the piston rod of the oil cylinder 6 moves from the large cavity to the small cavity, the hydraulic oil in the small cavity of the double-acting oil cylinder 6 is pressurized and then enters the large cavity of the execution oil cylinder 9 through the second check valve 4 to realize the increase of the piston rod of the execution oil cylinder 9. Press out. When the piston rod of the double-acting oil cylinder 6 runs to the limit position of the top of the small cavity, the detected position signal controls the second switching valve 5 to reset and switch to the lower position again, and the pressure oil of the working oil inlet 100 once again reduces the pressure of the double-acting oil cylinder 6 to the lower position. The cavity is filled with liquid, and through the repeated switching of the second switching valve 5 and the reciprocating motion of the double-acting oil cylinder 6, the execution oil cylinder 9 realizes the pressurization action during the continuous extension process.

When the execution cylinder 9 retracts after completing the extension, the pumped pressure oil is fed from port B, the third switching valve 8 is switched to the left position after the detected pressure signal feedback, and the hydraulic control check valve 7 is feeding It is opened under the action of oil pressure, and the pressure oil enters the small cavity of the execution oil cylinder 9 from the working oil return path 200 through the left position of the third switching valve 8, pushes the piston rod of the execution oil cylinder 9 to retract, and the large cavity of the execution oil cylinder 9 returns oil. The oil is returned from port A through the bypass oil path where the hydraulic control check valve 7 is located. The first check valve 3 and the second check valve 4 arranged on the working oil inlet 100 prevent the return oil from entering the double-acting oil cylinder. 6 within.

The above description is only one of the embodiments of the present invention, and for those skilled in the art, the present invention may have various modifications and variations. Any modification, substitution, improvement, etc. made within the claims of the present invention shall be included within the protection scope of the present invention.

Claims (10)

1. An acceleration booster system, characterized in that it comprises a second switching valve (5), a double-acting oil cylinder (6) and a third switching valve (8) arranged on the inlet and outlet oil passages of the execution oil cylinder; The inside of the double-acting oil cylinder (6) is a piston with a large end and a small end, and the large and small ends of the corresponding piston are respectively the large cavity and the small cavity of the double-acting oil cylinder, and the double-acting oil cylinder (6) passes through the large cavity and the small cavity. The small cavity and the branch are connected in parallel and arranged on the working oil inlet of the execution oil cylinder, and the second switching valve (5) is arranged on the branch connected with the large cavity of the double-acting oil cylinder (6); The third switching valve (8) is arranged on the working oil return line of the execution oil cylinder, and switches and connects the oil return port of the execution oil cylinder between the working oil return line and the working oil inlet line. 2 . The acceleration and supercharging system according to claim 1 , further comprising an accumulator ( 1 ), the accumulator ( 1 ) is connected and provided on the working oil inlet of the execution oil cylinder through a branch circuit, and the accumulator ( 1 ) The branch of (1) is provided with a first switching valve (2). 3 . The acceleration and supercharging system according to claim 2 , wherein the first switching valve ( 2 ) is a two-position two-way reversing valve, comprising a communication position and a cut-off position. 4 . 4. The acceleration booster system according to claim 1, wherein a hydraulic control check valve (7) connected in parallel with the double-acting oil cylinder (6) is further provided on the working oil inlet of the execution oil cylinder. The pilot oil circuit of the valve (7) is connected with the working oil return circuit of the actuating oil cylinder. 5. The acceleration and supercharging system according to claim 1, wherein the second switching valve (5) is a two-position three-way reversing valve, including a communication position and a cut-off position, and a double-acting switch is provided at the cut-off position. The large end of the oil cylinder (6) communicates with the two ends of the large cavity in an interconnected oil circuit. 6 . The acceleration and supercharging system according to claim 5 , wherein the large cavity of the double-acting oil cylinder ( 6 ) is connected to the working oil return circuit through an oil drain circuit on the side close to the small end. 7 . 7. The acceleration and supercharging system according to claim 1, wherein the third switching valve (8) is a two-position three-way reversing valve, comprising an oil return working position and a confluence working position, and the oil return working position will execute the The oil return port of the oil cylinder is communicated with the working oil return circuit, and the confluence working position communicates the oil return port of the execution oil cylinder with the working oil inlet circuit. 8. The acceleration booster system according to claim 4, wherein the parallel sections corresponding to the hydraulic control check valve (7) and the double-acting oil cylinder (6) on the working oil inlet are respectively provided with a first check valve (3) and the second check valve (4). 9. The acceleration and supercharging system according to any one of claims 2-8, wherein the first switching valve (2), the second switching valve (5) and the third switching valve (8) are hydraulically controlled reversing Both the first switching valve (2) and the third switching valve (8) are reversed by pilot pressure oil, and the second switching valve (5) is connected to the small valve of the double-acting oil cylinder (6) through a pilot oil circuit. cavity. 10. The acceleration and supercharging system according to any one of claims 2-8, wherein the first switching valve (2), the second switching valve (5) and the third switching valve (8) are electronically controlled reversing valve.

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