Gas-liquid supercharging device

Abstract

The utility model relates to a pressure increasing device, concretely relates to a gas-liquid pressure increasing device, the adjacent end connection of oil cylinder barrel and air cylinder barrel of same core arrangement is on the connecting seat, the cylinder end of oil cylinder barrel and air cylinder barrel away from each other is provided with oil cylinder cover, air cylinder cover respectively, the oil tank barrel for storing hydraulic oil is arranged closely with oil cylinder barrel, and the connecting seat has the through hole of the intercommunication of oil cylinder barrel cylinder cavity and oil tank barrel, and the accumulator that is arranged closely with oil outlet control valve is provided on oil cylinder cover. Oil tank barrel and oil cylinder barrel do not need lengthy oil pipe intercommunication, and the oil cylinder barrel oil supplement rate is higher. When the underpressure of executive spare part, the accumulator that is closer to oil outlet control valve can directly supply oil to the executive spare part and supplement pressure, and the accumulator can store certain oil pressure in advance, and need not plunger long distance reciprocating operation, can supplement pressure to the executive spare part in time. The utility model is in the lifting pump body oil supplement, pressure increasing response rate, and the pump body structure height integration and occupies small space, is favorable to the reasonable overall arrangement to the equipment in the limited space.

Description

Technical Field

[0001] This utility model patent relates to a pressurization device, specifically a gas-liquid pressurization device. Background Technology

[0002] A CNC machining center is a highly automated CNC machine tool that combines multiple processes such as milling and drilling, achieving cutting operations through table position adjustment and tool indexing and changing. The hydraulic power system, as a crucial component of CNC machine tools, plays a vital role. For example, in a patent document titled "Drilling and Milling Machining Center" (publication number CN111136491B), the turret indexing requires unlocking and locking via a locking mechanism. This locking mechanism, as the actuator, includes a cylinder, a piston, and a locking gear. By injecting or venting hydraulic oil or air into the cylinder, the cylinder is driven to move axially, causing the locking gear to engage or disengage with the limiting gear on the turret, thus achieving the indexing and fixing of the turret. In the past, hydraulic power was usually provided by large hydraulic stations, which often had multiple pipelines to provide hydraulic power to multiple machine tools. However, this resulted in the drawback of excessively long oil pipelines, which led to slow response of the actuators. Therefore, existing technologies also include a solution of equipping each machine tool with an independent pneumatic-hydraulic booster pump to provide hydraulic power. Pneumatic-hydraulic booster pumps have advantages such as small size, fast response, and automatic pressure compensation.

[0003] The patent document entitled "A Gas-Liquid Booster Pump" (publication number CN109854482B, hereinafter referred to as Document 1) discloses a technical solution including a first cylinder and a second cylinder. One end of the first cylinder is connected to a front cover, and the other end is connected to a rear cover. The second cylinder is connected to the front cover. The first cylinder has a first piston chamber, and the second cylinder has a second piston chamber. The first piston chamber contains a first piston and a piston rod, and the second piston chamber contains a second piston. The rear cover contains a reversing valve and a first connecting channel. A first buffer is located at the first connecting channel. A first vent pipe and a second vent pipe are located between the front cover and the rear cover. The front cover contains a second connecting channel, and a second buffer is located at the second connecting channel. The second cylinder is connected to an end cover with an inlet and a first check valve. The front cover has an outlet and a second check valve. This solution utilizes the reciprocating motion of the second piston within the second cylinder to achieve the inlet and outlet of pressurized oil.

[0004] The patent document entitled "A Single-Head Double-Acting Pneumatic-Liquid Booster Pump" (publication number CN110594117B, hereinafter referred to as Document 2) discloses a technical solution including a hydraulic high-pressure section and a pneumatic drive section. The hydraulic high-pressure section includes a flange cover, a front cover, an inlet check valve, a small cylinder, a small piston, a small piston check valve, a flange, and a transition flange guide end cover. The pneumatic drive section includes a pneumatic drive front cover, a pneumatic drive rear cover, a large cylinder, a large piston, a front pilot valve, a rear pilot valve, and a pneumatic slide valve. The large and small pistons are connected by piston rods fixed at both ends to the center of the piston. The pneumatic slide valve is located on the upper part of the pneumatic drive front cover. The pneumatic slide valve and the front and rear pilot valves ensure hydraulic oil output during the bidirectional movement of the piston, solving the problems of low efficiency due to the inability of traditional single-head single-acting pneumatic-liquid booster pumps to achieve continuous operation and the relatively high cost of double-head double-acting pneumatic-liquid booster pumps.

[0005] In the aforementioned technical solution, the pump body lacks an oil storage structure for supplying oil to the cylinder. Oil replenishment for the pneumatic-hydraulic booster pump must be drawn from a separately located oil storage structure (e.g., an oil tank) via pipelines. Considering the distance between the oil storage structure and the pump body, as well as the lengthy pipelines, this directly affects the replenishment cycle speed of the pump body and even the actuators. Therefore, the rational design of the oil storage structure has a significant impact on the pump's rapid and stable pressurization. Furthermore, when the actuators are under-pressurized, replenishment and pressurization are achieved through piston movement. However, considering that one pressurization cycle requires one piston reciprocation and the piston stroke is long, this also affects the pressurization response rate of the actuators and needs improvement. Additionally, because the hydraulic pump and oil tank are spatially separate independent units, their large space occupation and difficulty in effective integration make it impossible to adapt them independently to machining centers. Utility Model Content

[0006] This invention provides a gas-liquid booster device that improves the integration of the oil cylinder with its connected oil tank and accumulator, thereby reducing its space occupation and improving the pressure response rate of the actuator.

[0007] To achieve the above objectives, the technical solution adopted is as follows: a gas-liquid booster device, wherein the adjacent ends of concentrically arranged hydraulic cylinders and pneumatic cylinders are connected to a connecting seat, and the ends of the hydraulic cylinders and pneumatic cylinders that are far apart from each other are respectively provided with hydraulic cylinder covers and pneumatic cylinder covers, and one end of a plunger inserted into a through hole on the connecting seat extends into the hydraulic cylinder, while the other end of the plunger is located in the pneumatic cylinder. A sealed sliding fit is formed between the plunger and the through hole on the connecting seat. The end of the plunger located in the pneumatic cylinder has a piston, and a sealing ring is provided on the circumferential surface of the piston to divide the cylinder cavity into two gas chambers. The circumferential surface of the plunger and the hydraulic cylinder are connected. The cylinder wall clearance arrangement is such that the inner diameter of the air cylinder is larger than that of the oil cylinder. The oil tank for storing hydraulic oil is arranged adjacent to the oil cylinder. The connecting seat has a connecting hole that connects to the cylinder cavity. The output end of the first check valve, which is set in the connecting hole, is connected to the cylinder cavity, and the input end is connected to the oil outlet of the oil tank. The cylinder cover is provided with a pressure oil drain hole. A second check valve is set in the pressure oil drain hole. The input end of the second check valve is connected to the cylinder cavity, and the output end of the second check valve is connected to the inlet of the accumulator and the oil outlet control valve set on the cylinder cover.

[0008] Compared with existing technologies, the technical advantages of this invention are as follows: the oil tank for storing hydraulic oil is arranged adjacent to the cylinder barrel, and a connecting hole connecting the oil tank and the cylinder barrel is provided on the connecting seat, eliminating the need for lengthy oil pipes and resulting in a higher oil replenishment rate for the cylinder barrel. Simultaneously, an accumulator is installed on the cylinder head. When the actuator is under-pressurized, the accumulator, which is closer to the oil outlet control valve, can directly supply oil to replenish the actuator. The accumulator can also pre-store a certain amount of oil pressure, eliminating the need for long-distance reciprocating operation of the plunger, thus effectively improving the pressure replenishment response rate of the actuator. While improving the pump body's oil replenishment and pressure boosting response rate, this invention also features a highly integrated pump body structure with a small footprint, facilitating rational and coordinated equipment layout within limited space and easy integration with machining centers. Attached Figure Description

[0009] Figure 1 This is a three-dimensional appearance schematic diagram of the present utility model;

[0010] Figure 2 This is a side view of the present invention;

[0011] Figure 3 This is a top view of the present invention;

[0012] Figure 4 for Figure 3 KK-direction sectional view in the middle;

[0013] Figure 5 for Figure 3 LL-direction sectional view;

[0014] Figure 6 for Figure 5A schematic diagram of a local structure in the image;

[0015] Figure 7 This is a schematic diagram of the working port connection for the oil outlet control valve. Detailed Implementation

[0016] The following is in conjunction with the appendix Figure 1-7 The present invention will be further described in detail below, including related content:

[0017] A gas-liquid booster device includes a hydraulic cylinder 10 and a pneumatic cylinder 20 arranged concentrically, with their adjacent ends connected to a connecting seat 30. The cylinder ends of the hydraulic cylinder 10 and pneumatic cylinder 20, which are spaced apart, are respectively provided with a cylinder head 40 and a pneumatic cylinder head 50. A plunger 21, which passes through a hole in the connecting seat 30, has one end extending into the hydraulic cylinder 10 and the other end located inside the pneumatic cylinder 20. A sealed sliding fit is formed between the plunger 21 and the through hole in the connecting seat 30. A piston 22 is located at the end of the plunger 21 inside the pneumatic cylinder 20. A sealing ring is provided on the circumference of the piston 22 to divide the cavity of the pneumatic cylinder 20 into two gas chambers. The circumference of the plunger 21 is spaced apart from the wall of the hydraulic cylinder 10. The inner diameter of cylinder 20 is larger than that of cylinder 10. The oil tank 60, which is used to store hydraulic oil, is arranged adjacent to cylinder 10. The connecting seat 30 has a connecting hole 31 that connects to the cylinder cavity of cylinder 10. The output end of the first check valve 311, which is set in the connecting hole 31, is connected to the cylinder cavity of cylinder 10, and the input end is connected to the oil outlet of oil tank 60. The cylinder cover 40 is provided with a pressure oil drain hole 41. A second check valve 411 is provided in the pressure oil drain hole 41. The input end of the second check valve 411 is connected to the cylinder cavity of cylinder 10, and the output end of the second check valve 411 is connected to the accumulator 70 and the oil outlet control valve 80 on the cylinder cover 40.

[0018] In the above technical solution, the oil tank 60 for storing hydraulic oil is arranged adjacent to the cylinder 10, and a connecting hole 31 is provided on the connecting seat 30 to connect the oil tank 60 and the cylinder 10, eliminating the need for a long oil pipe. The oil in the oil tank 60 directly enters the cylinder 10 through the connecting hole 31, allowing for faster oil replenishment in the cylinder 10. Simultaneously, an accumulator 70 is installed on the cylinder cover 40. When the actuator is under-pressurized, the accumulator 70, being closer to the oil outlet control valve 80, can directly supply oil to replenish the actuator. The accumulator 70 can also pre-store a certain amount of oil pressure, thus eliminating the need for the plunger 21 to reciprocate over long distances and providing timely pressure replenishment to the actuator, effectively improving the pressure replenishment response rate. This utility model improves the pump's oil replenishment and pressure boosting response rate while maintaining a highly integrated pump structure and occupying little space, facilitating reasonable overall equipment layout within limited space and easy integration with machining centers.

[0019] It should be noted that for traditional gas-liquid booster pumps without accumulator 70, to ensure stable pressure on the actuator, the cylinder 20 needs to be constantly in an intake state, meaning compressed gas must continuously enter the cylinder 20 to maintain force balance and a stationary state for the piston 22 and plunger 21. If the actuator experiences underpressure, the force balance is disrupted, and the piston 22 and plunger 21 will automatically move under the action of compressed gas to replenish pressure. Therefore, this solution has high energy consumption, and if the intake mechanism malfunctions, the equipment cannot replenish pressure in time, posing a safety hazard. In contrast, this solution, with the accumulator 70, eliminates the need for the cylinder 20 to continuously maintain an intake, resulting in relatively lower energy consumption. Furthermore, even if the intake mechanism malfunctions, the pre-stored oil pressure in the accumulator 70 can ensure stable actuator pressure for a short period, greatly facilitating pump maintenance without continuous pressure reduction.

[0020] In addition, with Figure 4 Taking the oil inlet and outlet method of cylinder 10 as an example, a certain amount of atmospheric pressure oil is injected into the oil tank 60 beforehand. When the piston 22 in cylinder 20 moves upward, the plunger 21 gradually enters the cylinder cavity of cylinder 10, squeezing the oil in cylinder 10 to form pressurized oil. The pressurized oil can be output to the actuator through the pressurized oil drain hole 41 on the cylinder cover 40 to drive the actuator. The second one-way valve 411 prevents the oil delivered to the actuator from flowing back into cylinder 10 through the pressurized oil drain hole 41. Subsequently, when the piston 22 moves downward, the plunger 21 moves from cylinder 10 into cylinder 20, the oil cavity space in cylinder 10 expands, and a negative pressure is formed in cylinder 10. This allows the oil stored in the oil tank 60 to be drawn into cylinder 10 through the connecting hole 31, thus replenishing the oil in cylinder 10. The first check valve 311 prevents the oil in the cylinder 10 from flowing back into the tank 60 when the plunger 21 moves upward.

[0021] Here, since the intake mechanism of a traditional pneumatic-hydraulic booster pump is already clearly described in existing technology, it is considered prior art. The intake mechanism mainly includes a pneumatic slide valve and a reversing valve (or pilot valve). Taking the structure of this application as an example, a reversing valve is installed on the opposite side of the connecting seat 30 and the cylinder head 50. The pneumatic slide valve controls the intake of air into the upper or lower chamber of the piston 22. For example, when the pneumatic slide valve intakes air into the lower chamber of the piston 22, the piston 22 moves upward, and simultaneously, the upper chamber of the piston 22 exhausts air. When the piston 22 moves upward to press against the reversing valve on the connecting seat 30, it changes the intake channel of the pneumatic slide valve, causing the upper chamber of the piston 22 to begin intake, while the lower chamber of the piston 22 begins exhaust, driving the piston 22 downward. Conversely, when the piston 22 presses against the reversing valve on the cylinder head 50, the lower chamber of the piston 22 receives air again, and the upper chamber exhausts air. This cycle continues, driving the piston 22 and the plunger 21 to reciprocate. In addition, the intake and exhaust of the upper and lower chambers of piston 22 can also be controlled electronically, and the stroke of piston 22 and the output oil pressure of pump body can be detected.

[0022] As a preferred embodiment, the tubular oil tank 60 is sleeved around the cylinder 10 and both ends of the oil tank 60 are connected to the connecting seat 30 and the cylinder cover 40, respectively. An annular cavity C for storing hydraulic oil is formed between the oil tank 60 and the cylinder 10, and the input end of the first one-way valve 311 is connected to the annular cavity C.

[0023] In this design, a tubular oil tank 60 is fitted around the outer periphery of the cylinder 10. The cylinder cover 40, connecting seat 30, cylinder wall of cylinder 10 and cylinder wall of oil tank 60 of the gas-liquid booster pump cooperate with each other to directly form a hydraulic oil storage cavity (i.e., annular cavity C) that is arranged adjacent to and attached to the cylinder 10. The annular cavity C is formed based on the structure of the cylinder 10 itself. At the same time, there is no need for a long oil pipe to connect the oil tank 60 and the cylinder 10. The available space on the pump body structure is fully utilized to integrate the oil storage structure. The oil storage structure is highly integrated with the pump body and has a small volume, making the oil replenishment and pressurization response of the cylinder 10 faster.

[0024] Furthermore, the output end of the connecting hole 31 is connected to the gap between the circumference of the plunger 21 and the inlet of the cylinder barrel 10. This gap forms an oil inlet channel for the cylinder barrel 10. On the one hand, it eliminates the need to machine an oil inlet hole on the cylinder barrel 10, ensuring the structural strength of the cylinder barrel 10. On the other hand, it eliminates the need for pipelines, making the structure simpler.

[0025] As a preferred embodiment, the hydraulic cylinder 10 and the pneumatic cylinder 20 are vertically distributed and erected as a whole. A replenishment tank 90 is connected to the connecting seat 30. The oil drain hole 91 at the bottom of the replenishment tank 90 is connected to the annular cavity C via an oil passage hole 32 on the connecting seat 30. An air vent is provided on the top of the replenishment tank 90. ​​In this embodiment, considering the continuous decrease in oil within the annular cavity C, oil needs to be added; therefore, a replenishment tank 90 is provided. By opening the cover of the replenishment tank 90 and adding oil, the added oil enters the annular cavity C through the oil drain hole 91 at the bottom of the tank, thus facilitating the replenishment of oil to the annular cavity C. The air vent on the top of the replenishment tank 90 is provided to prevent negative pressure from forming when the oil level in the tank decreases, which could hinder the subsequent discharge of oil.

[0026] Furthermore, to prevent negative pressure from forming inside the annular cavity C during the process of oil entering the cylinder 10, which would make it difficult for oil to enter the cylinder 10, a vent 42 is provided on the cylinder cover 40 to connect the annular cavity C with the atmospheric environment, so that the annular cavity C is always a normal pressure cavity. A breathing membrane 421 is provided inside the vent 42 to prevent external particulate pollutants from entering the annular cavity C through the vent 42 and contaminating the oil.

[0027] Combination Figure 5 and Figure 7 As shown, the oil outlet control valve 80 is a solenoid valve and the valve body is respectively provided with a first working port A, a second working port B, an oil inlet P and an oil return port T. The first working port A and the second working port B are connected to the actuator. The oil return port T is connected to the annular cavity C through the oil return hole 43 on the cylinder cover 40. The lower end of the oil return hole 43 is connected to a through pipe O. The lower end of the through pipe O extends downward to a position near the connecting seat 30.

[0028] In this design, the oil outlet control valve 80 is directly integrated into the cylinder head 40. The oil outlet control valve 80 and the cylinder head 40 do not require a lengthy pipeline connection, thus shortening the oil flow path to a certain extent and helping to improve the response rate of the pump body's oil replenishment and pressurization. In addition, a through pipe O is provided at the lower end of the oil return hole 43, which can better guide the returning oil to the bottom of the annular cavity C, suppressing the phenomenon of foaming caused by the oil discharged from the oil return hole 43 impacting the annular cavity C. This is to ensure a stable oil supply inside the cylinder barrel 10 and to prevent the oil in the annular cavity C from forming a foam layer due to foaming and being discharged through the vent hole 42 on the cylinder head 40.

[0029] In addition, the oil outlet control valve 80 is a two-position four-way valve. The valve body's structure is existing technology and will not be discussed in detail here. To better understand the oil flow between the pump body and the actuator, the basic control concept of the oil outlet control valve 80 is explained below: The pressurized oil discharged from the pressurized oil drain hole 41 enters the oil inlet P of the oil outlet control valve 80. The oil outlet control valve 80 controls the pressurized oil to be delivered to the actuator through either the first working port A or the second working port B. When the first working port A supplies oil to the actuator, the actuator simultaneously returns oil to the pump body through the second working port B (the oil inlet and outlet actions of the actuator can be referenced from the oil inlet and outlet actions of a traditional hydraulic cylinder). Conversely, when the second working port B supplies oil to the actuator, the first working port A simultaneously returns oil. In this process, whether it is the first working port A or the second working port B that returns oil, the oil returned by the actuator will be discharged through the oil return port T on the oil outlet control valve 80, and further discharged directly into the annular cavity C through the oil return hole 43 on the cylinder cover 40 and the through pipe O, for subsequent pump body pressurization. In this way, the actuator and the pump body form an oil circulation path through the oil outlet control valve 80, without the need to continuously replenish oil through the oil replenishment tank 90.

[0030] Combination Figure 5 and Figure 6 As shown, the cylinder cover 40 has a first oil passage 44a and a second oil passage 44b that are interconnected. The input ends of the first oil passage 44a and the second oil passage 44b are both connected to the output end of the second check valve 411. The output end of the first oil passage 44a is connected to the accumulator 70, and the output end of the second oil passage 44b is connected to the oil inlet P of the oil outlet control valve 80.

[0031] This solution provides a detailed description of the common oil passage within the accumulator 70. The first oil passage 44a serves as both the oil inlet and outlet passage for the accumulator 70. When the outlet control valve 80 is closed, the reciprocating motion of the plunger 21 drives the cylinder 10 to receive and discharge oil, thereby charging the accumulator 70. Specifically, pressurized oil enters the accumulator 70 through the first oil passage 44a. When the outlet control valve 80 is opened, the pressurized oil within the accumulator 70 is discharged through the first oil passage 44a and enters the outlet control valve 80 through the connected second oil passage 44b, thus supplying oil to the actuators.

[0032] Furthermore, the cylinder cover 40 is provided with a third oil passage 44c and an oil drain passage 44d. The third oil passage 44c is connected to the output end of the second one-way valve 411, and the oil drain passage 44d is connected to the annular cavity C. The cylinder cover 40 is provided with a pressure relief valve 100. When the pressure relief valve 100 is opened / closed, the third oil passage 44c and the oil drain passage 44d are connected / blocked.

[0033] In this design, since the third oil passage 44c is connected to the output end of the second check valve 411, the third oil passage 44c is also connected to the first oil passage 44a and the second oil passage 44b. With the pressure relief valve 100 in place, when the pump body needs to be inspected and maintained, the pressure relief valve 100 is opened to connect the third oil passage 44c with the oil discharge passage 44d, which can release the pressure in the accumulator 70 and the oil passages in the cylinder head 40, making inspection and maintenance convenient.

[0034] As a preferred solution, to monitor the pressure in the oil passages within the cylinder head 40, a pressure gauge 110 is installed on the cylinder head 40 to monitor the oil pressure in the third oil passage 44c. When the pressure displayed by the pressure gauge 110 is below the standard, the oil passages within the cylinder head 40 and the accumulator 70 can be pressurized by reciprocating the plunger 21. Alternatively, it can be used in conjunction with the pressure relief valve 100 to determine whether the pressure within the pump body has been completely released before performing pump maintenance and repair work, ensuring operational safety.

[0035] As a preferred embodiment, to facilitate the disassembly and fixation of the second check valve 411, the pressure oil drain hole 41 is a stepped straight-through hole with a smaller inner diameter and a larger outer diameter, penetrating the inner and outer end faces of the cylinder head 40. A plug 412 is installed inside the outer end of the pressure oil drain hole 41, and the inner end of the plug 412 is clamped between the stepped surface of the pressure oil drain hole 41 and the opposite end face of the second check valve 411. When it is necessary to disassemble the second check valve 411, the plug 412 is removed, and the second check valve 411 can be taken out from the larger diameter end of the pressure oil drain hole 41. Conversely, the second check valve 411 is inserted from the larger diameter end of the pressure oil drain hole 41, and the plug 412 and the stepped surface of the pressure oil drain hole 41 limit the check valve 411, thus fixing the check valve 411.

[0036] Furthermore, the plug 412 is tubular in shape, and its cavity forms the first oil passage 44a. The inner end of the plug 412 is connected to the output end of the second one-way valve 411, and the outer end of the plug 412 is connected to the accumulator 70. In this design, the plug 412 serves both as a limiting component for fixing the second one-way valve 411 and as a connecting component between the accumulator 70 and the cylinder head 40. This improves the integration between the accumulator 70 and the cylinder head 40, while also helping to reduce the number of oil passages arranged inside the cylinder head 40 and reducing the manufacturing difficulty of the cylinder head 40.

Claims

1. A gas-liquid booster device, wherein the adjacent ends of a concentrically arranged oil cylinder (10) and a pneumatic cylinder (20) are connected to a connecting seat (30), and the cylinder ends of the oil cylinder (10) and the pneumatic cylinder (20) which are far apart from each other are respectively provided with an oil cylinder cover (40) and a pneumatic cylinder cover (50), one end of a plunger (21) inserted into a through hole on the connecting seat (30) extends into the oil cylinder (10) and the other end is located in the pneumatic cylinder (20), and a sealed sliding fit is formed between the plunger (21) and the through hole on the connecting seat (30), and a piston (22) is provided at the end of the plunger (21) located in the pneumatic cylinder (20), and a sealing ring is provided on the circumferential surface of the piston (22) to divide the cylinder cavity of the pneumatic cylinder (20) into two gas chambers, the gap between the circumferential surface of the plunger (21) and the cylinder wall of the oil cylinder (10) is arranged, and the inner diameter of the pneumatic cylinder (20) is larger than the inner diameter of the oil cylinder (10), characterized in that: The oil tank (60) for storing hydraulic oil is arranged close to the cylinder (10). The connecting seat (30) has a connecting hole (31) that connects to the cylinder cavity of the cylinder (10). The output end of the first check valve (311) set in the connecting hole (31) is connected to the cylinder cavity of the cylinder (10), and the input end is connected to the oil outlet of the oil tank (60). The cylinder cover (40) is provided with a pressure oil drain hole (41). The pressure oil drain hole (41) is provided with a second check valve (411). The input end of the second check valve (411) is connected to the cylinder cavity of the cylinder (10), and the output end of the second check valve (411) is connected to the accumulator (70) and the oil outlet control valve (80) set on the cylinder cover (40).

2. The gas-liquid booster device according to claim 1, characterized in that: A tubular oil tank (60) is fitted around the cylinder (10) and both ends of the oil tank (60) are connected to the connecting seat (30) and the cylinder cover (40) respectively. An annular cavity (C) for storing hydraulic oil is formed between the oil tank (60) and the cylinder (10). The input end of the first check valve (311) is connected to the annular cavity (C).

3. The gas-liquid booster device according to claim 2, characterized in that: The output end of the connecting hole (31) is connected to the gap between the circumference of the plunger (21) and the opening of the cylinder barrel (10).

4. The gas-liquid booster device according to claim 2 or 3, characterized in that: The oil cylinder (10) and the air cylinder (20) are distributed vertically and are placed vertically as a whole. The oil tank (90) is connected to the connecting seat (30). The oil drain hole (91) at the bottom of the oil tank (90) and the annular cavity (C) are connected through the oil passage hole (32) on the connecting seat (30). The top of the oil tank (90) is provided with an air hole.

5. The gas-liquid booster device according to claim 4, characterized in that: The cylinder cover (40) has a vent (42) that connects the annular cavity (C) to the atmospheric environment, and a breathing membrane (421) is installed inside the vent (42).

6. The gas-liquid booster device according to claim 2, characterized in that: The oil outlet control valve (80) is a solenoid valve and the valve body is provided with a first working port (A), a second working port (B), an oil inlet (P) and an oil return port (T). The first working port (A) and the second working port (B) are connected to the actuator. The oil return port (T) and the annular cavity (C) are connected through the oil return hole (43) on the cylinder cover (40). The lower end of the oil return hole (43) is connected to a through pipe (O). The lower end of the through pipe (O) extends downward to a position near the connecting seat (30).

7. The gas-liquid booster device according to claim 1, characterized in that: The cylinder cover (40) has a first oil passage (44a) and a second oil passage (44b) that are interconnected. The input ends of the first oil passage (44a) and the second oil passage (44b) are connected to the output end of the second check valve (411). The output end of the first oil passage (44a) is connected to the accumulator (70), and the output end of the second oil passage (44b) is connected to the oil inlet (P) of the oil outlet control valve (80).

8. The gas-liquid booster device according to claim 2, characterized in that: The cylinder head (40) has a third oil passage (44c) and an oil drain passage (44d) inside its cover. The third oil passage (44c) is connected to the output end of the second check valve (411), and the oil drain passage (44d) is connected to the annular cavity (C). The cylinder head (40) is equipped with a pressure relief valve (100). When the pressure relief valve (100) is opened / closed, the third oil passage (44c) and the oil drain passage (44d) are connected / blocked.

9. The gas-liquid booster device according to claim 8, characterized in that: A pressure gauge (110) is provided on the cylinder head (40) for monitoring the oil pressure in the third oil passage (44c).

10. The gas-liquid booster device according to claim 7, characterized in that: The pressure oil drain hole (41) is a stepped straight hole with a small inner diameter and a large outer diameter, which penetrates the inner and outer end faces of the cylinder cover (40). A plug (412) is provided inside the outer end of the pressure oil drain hole (41). The inner end of the plug (412) and the stepped surface of the pressure oil drain hole (41) are sandwiched on the opposite side end face of the second check valve (411).

11. The gas-liquid booster device according to claim 10, characterized in that: The plug (412) is tubular in shape and its cavity forms the first oil passage (44a). The inner end of the plug (412) is connected to the output end of the second check valve (411), and the outer end of the plug (412) is connected to the accumulator (70).

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