Gas-liquid supercharging device

Abstract

The invention relates to a supercharging device, in particular to a gas-liquid supercharging device, which is characterized in that the near ends of an oil cylinder barrel and an air cylinder barrel which are concentrically arranged are connected to a connecting seat, the barrel ends of the oil cylinder barrel and the air cylinder barrel which are far away from each other are respectively provided with an oil cylinder cover and an air cylinder cover, and an oil tank barrel for storing hydraulic oil is arranged adjacent to the oil cylinder barrel; a communicating hole for communicating the cylinder cavity of the oil cylinder barrel with the oil tank barrel is formed in the connecting seat; and meanwhile, an energy accumulator adjacent to the oil outlet control valve is arranged on the oil cylinder cover. The oil tank barrel and the oil cylinder barrel do not need to be communicated through a lengthy oil pipe, and the oil supplementing speed of the oil cylinder barrel is higher. When the executing part is under-pressure, the energy accumulator closer to the oil outlet control valve can directly supply oil to the executing part to supplement pressure, meanwhile, certain oil pressure can be stored in the energy accumulator in advance, and pressure can be supplemented to the executing part in time without long-distance reciprocating motion of the plunger. While the oil supplementing and pressurizing response rate of the pump body is increased, the pump body structure is highly integrated, the occupied space is small, and reasonable overall arrangement of equipment in a limited space is facilitated.

Description

TECHNICAL FIELD

[0001] The present application relates to a supercharging device, in particular to a gas-liquid supercharging device. BACKGROUND

[0002] The numerical control machine tool machining center is a numerical control machine tool with extremely high automation, which can combine various processes such as milling and drilling, and realize cutting processing by combining the position adjustment of the workbench and the indexing tool changing. Among them, the hydraulic power system as an important part of the numerical control machine tool plays an extremely important role. For example, in the patent literature with the name "drilling and milling machining center" (publication number CN111136491B), the indexing of the tool tower needs to be unlocked and locked through the locking mechanism. The locking mechanism as an actuator includes a cylinder body, a piston and a locking tooth disc. By injecting and discharging hydraulic oil or air into the cylinder body, the cylinder body is driven to move axially, driving the locking tooth disc to engage or separate from the limiting tooth disc on the tool tower, and realizing the indexing of the tool tower. In the past technology, the hydraulic pressure is usually provided by a large hydraulic station, and the hydraulic station often sets up multiple pipelines to provide hydraulic power for multiple machine tools, but this corresponds to the defect that the oil pipeline is too long, so that the actuator responds slowly. Therefore, in the prior art, there is also a scheme of separately providing an independent gas-liquid supercharging pump for each machine tool to provide hydraulic power. The gas-liquid supercharging pump has the advantages of small size, fast response and automatic pressure compensation.

[0003] The patent literature with the name "a gas-liquid supercharging pump" (publication number CN109854482B, hereinafter referred to as document 1) discloses a technical scheme including a first cylinder and a second cylinder, the first cylinder is connected with a front cover at one end and connected with a rear cover at the other end, the second cylinder is connected to the front cover, the first cylinder is provided with a first piston cavity, the second cylinder is provided with a second piston cavity, the first piston cavity is provided with a first piston and a piston rod, the second piston cavity is provided with a second piston, the rear cover is provided with a reversing valve, the rear cover is provided with a first connecting channel, the first connecting channel is provided with a first buffer, the front cover and the rear cover are provided with a first air pipe and a second air pipe, the front cover is provided with a second connecting channel, the second connecting channel is provided with a second buffer, the second cylinder is connected with an end cover, the end cover is provided with a liquid inlet, the end cover is further provided with a first check valve, the front cover is provided with a liquid outlet, and the front cover is provided with a second check valve. The scheme uses the reciprocating movement of the second piston in the second cylinder to realize the oil inlet and oil outlet of the pressure oil;

[0004] The technical scheme disclosed in the patent document with the title of "Single-head double-acting gas-liquid booster pump" (publication number CN110594117B, hereinafter referred to as document 2) includes a hydraulic high-pressure part and a gas drive part, wherein the hydraulic high-pressure part includes a flange gland, a front end cover, an oil inlet check valve, a small cylinder, a small piston, a small piston check valve, a method flange, and a transition flange guide end cover; the gas drive part includes a gas drive front end cover, a gas drive rear end cover, a large cylinder, a large piston, a front pilot valve, a rear pilot valve, and a pneumatic spool valve, the large and small pistons are connected through a piston rod fixed at the center part of the piston at both ends, and the pneumatic spool valve is located on the upper part of the gas drive front end cover. The setting of the pneumatic spool valve and the front and rear pilot valves makes the hydraulic oil be output during the bidirectional movement of the piston, solving the problems of low efficiency of the traditional single-head single-acting gas-liquid booster pump which cannot realize continuous work and the relatively high cost of the double-head double-acting gas-liquid booster pump.

[0005] In the above technical scheme, the pump body does not have an oil storage structure for supplying oil to the oil cylinder, and the oil supplement of the gas-liquid booster pump needs to be extracted from a separately arranged oil storage structure (such as an oil tank) through a pipeline. Considering the distance between the oil storage structure and the pump body and the long pipeline factor, which will directly affect the oil supplement rhythm of the pump body and even the actuator, how to reasonably arrange the oil storage structure has a non-negligible influence on the rapid and stable pressure boosting of the pump body. Moreover, when the actuator is underpressure, oil supplement and pressure boosting need to be performed through the movement of the piston. However, considering that the piston needs to move back and forth once to realize pressure boosting once and the piston movement stroke is long, this also affects the pressure supplement response rate of the actuator, which needs to be improved. In addition, since the hydraulic pump and the oil tank are completely separated independent units in space, they occupy a large space and are difficult to integrate effectively, which cannot be adapted to machining centers alone. SUMMARY

[0006] The present application provides a gas-liquid pressure boosting device, which improves the integration of the oil cylinder and the oil tank and the accumulator connected thereto, reduces the space occupied, and improves the pressure supplement response rate of the actuator.

[0007] In order to achieve the above object, the technical scheme adopted is: a gas-liquid supercharging device, the adjacent ends of the oil cylinder barrel and the gas cylinder barrel arranged in the same core are connected on the connecting seat, the cylinder ends of the oil cylinder barrel and the gas cylinder barrel away from each other are respectively provided with an oil cylinder cover and a gas cylinder cover, one end of the plunger passing through the through hole in the connecting seat extends into the oil cylinder barrel, the other end of the plunger is located in the gas cylinder barrel, the plunger and the through hole in the connecting seat form a sealed sliding fit, the end of the plunger located in the gas cylinder barrel is provided with a piston, the sealing ring is arranged on the peripheral surface of the piston to separate the cylinder cavity of the gas cylinder barrel into two gas chambers, the peripheral surface of the plunger is arranged in a gap with the cylinder wall of the oil cylinder barrel, the inner diameter of the gas cylinder barrel is larger than the inner diameter of the oil cylinder barrel, the oil tank barrel for storing hydraulic oil is arranged in close proximity to the oil cylinder barrel, the connecting seat is provided with a communication hole communicating with the cylinder cavity of the oil cylinder barrel, the output end of the first one-way valve arranged in the communication hole communicates with the cylinder cavity of the oil cylinder barrel, and the input end of the first one-way valve communicates with the oil outlet hole of the oil tank barrel.

[0008] Compared with the prior art, the technical effect of the present application is that the oil tank barrel for storing hydraulic oil is arranged in close proximity to the oil cylinder barrel, and the communication hole communicating the oil tank barrel and the oil cylinder barrel is arranged on the connecting seat, the long oil pipe is cancelled, and the oil supplementing rate of the oil cylinder barrel is higher. At the same time, the accumulator is arranged on the oil cylinder cover, when the pressure of the actuator is insufficient, the accumulator closer to the oil outlet control valve can directly supply oil to the actuator to supplement the pressure, and the accumulator can store a certain oil pressure in advance, so that the actuator can be supplemented in time without long-distance reciprocating operation of the plunger, thereby effectively improving the response rate of the actuator to supplement the pressure. While improving the oil supplementing and pressure increasing response rate of the pump body, the pump body is highly integrated and occupies a small space, which is beneficial to the reasonable overall arrangement of the equipment in a limited space and facilitates the separate adaptation with the machining center. BRIEF DESCRIPTION OF DRAWINGS

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

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

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

[0012] Figure 4 is Figure 3 the K-K sectional view in

[0013] Figure 5 is Figure 3 the L-L sectional view in

[0014] Figure 6 is Figure 5The local structure schematic view in the figure;

[0015] Figure 7 The working port connection schematic view of the oil outlet control valve. DETAILED DESCRIPTION

[0016] The application will be further described in detail below in combination with the accompanying Figures 1-7 and related contents:

[0017] A gas-liquid pressurizing device, the oil cylinder barrel 10 and the gas cylinder barrel 20 arranged in the same core are connected to the connecting seat 30 at the adjacent ends, the cylinder ends of the oil cylinder barrel 10 and the gas cylinder barrel 20 away from each other are respectively provided with an oil cylinder cover 40 and a gas cylinder cover 50, one end of the plunger 21 passing through the through hole in the connecting seat 30 extends into the oil cylinder barrel 10, and the other end of the plunger 21 is located in the gas cylinder barrel 20, the plunger 21 and the through hole in the connecting seat 30 form a sealed sliding fit, the end of the plunger 21 located in the gas cylinder barrel 20 is provided with a piston 22, the piston 22 is provided with a sealing ring on the peripheral surface to separate the cylinder cavity of the gas cylinder barrel 20 into two gas chambers, the plunger 21 is arranged in a gap between the peripheral surface of the plunger 21 and the cylinder wall of the oil cylinder barrel 10, the inner diameter of the gas cylinder barrel 20 is greater than the inner diameter of the oil cylinder barrel 10, and the oil tank barrel 60 for storing hydraulic oil is arranged in close proximity to the oil cylinder barrel 10, the connecting seat 30 is provided with a communication hole 31 communicating with the cylinder cavity of the oil cylinder barrel 10, and the output end of the first one-way valve 311 arranged in the communication hole 31 communicates with the cylinder cavity of the oil cylinder barrel 10, and the input end of the first one-way valve 311 communicates with the oil outlet hole of the oil tank barrel 60; the oil cylinder cover 40 is provided with a pressure oil discharge hole 41, the pressure oil discharge hole 41 is provided with a second one-way valve 411, the input end of the second one-way valve 411 communicates with the cylinder cavity of the oil cylinder barrel 10, and the output end of the second one-way valve 411 and the oil inlet port P of the energy accumulator 70 and the oil outlet control valve 80 arranged on the oil cylinder cover 40 are commonly communicated with each other.

[0018] In the above technical solution, the oil tank barrel 60 for storing hydraulic oil is arranged in close proximity to the oil cylinder barrel 10, and the communication hole 31 communicating the oil tank barrel 60 and the oil cylinder barrel 10 is arranged on the connecting seat 30, so that the long oil pipe is cancelled, the oil liquid in the oil tank barrel 60 directly enters the oil cylinder barrel 10 through the communication hole 31, and the oil cylinder barrel 10 is replenished faster. At the same time, the energy accumulator 70 is arranged on the oil cylinder cover 40, when the actuator is under pressure, the energy accumulator 70 closer to the oil outlet control valve 80 can directly supply oil to the actuator to compensate the pressure, and the energy accumulator 70 can store a certain oil pressure in advance, so that the plunger 21 does not need to operate for a long distance, and the actuator can be compensated in time, and the response rate of the actuator is effectively improved. While improving the oil replenishment and pressure response rate of the pump body, the pump body structure is highly integrated and occupies a small space, which is conducive to the reasonable overall arrangement of the equipment in a limited space and facilitates the separate adaptation with the machining center.

[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 air inlet mechanism of the conventional gas-liquid booster pump is clearly described in the prior art, it belongs to the prior art, and the air inlet mechanism is briefly introduced. The air inlet mechanism mainly includes a pneumatic slide valve and a reversing valve (or called a pilot valve). For example, the structure of the present application, the reversing valve is arranged on the opposite side of the connecting seat 30 and the cylinder cover 50, and the pneumatic slide valve is used to control the air inlet of the upper chamber or the lower chamber of the piston 22. For example, when the pneumatic slide valve supplies air to the lower chamber of the piston 22, the piston 22 goes up, and at the same time, the upper chamber of the piston 22 exhausts. When the piston 22 goes up to the reversing valve on the connecting seat 30, the air inlet channel of the pneumatic slide valve changes, so that the upper chamber of the piston 22 starts to supply air, and the lower chamber of the piston 22 starts to exhaust, driving the piston 22 to go down. Conversely, when the piston 22 is pressed against the reversing valve on the cylinder cover 50, the lower chamber of the piston 22 supplies air again and the upper chamber exhausts, so as to drive the piston 22 and the plunger 21 to reciprocate. In addition, the air inlet and outlet of the upper and lower chambers of the piston 22 can also be controlled by electric control, and the stroke of the piston 22 and the detection of the output oil pressure of the pump body can be determined.

[0022] As a preferred solution, the tubular oil tank cylinder 60 is sleeved on the outer periphery of the oil cylinder cylinder 10, and the two ends of the oil tank cylinder 60 are connected to the connecting seat 30 and the oil cylinder cover 40 respectively, and the annular pipe cavity C for storing hydraulic oil is formed between the oil tank cylinder 60 and the oil cylinder cylinder 10. The input end of the first one-way valve 311 communicates with the annular pipe cavity C.

[0023] In this solution, the tubular oil tank cylinder 60 is sleeved on the outer periphery of the oil cylinder cylinder 10, and the cylinder wall of the oil cylinder cover 40, the connecting seat 30 and the oil cylinder cylinder 10 cooperates with the cylinder wall of the oil tank cylinder 60 to directly enclose the hydraulic oil storage pipe cavity (i.e. the annular pipe cavity C) which is arranged adjacent to the oil cylinder cylinder 10 and depends on the oil cylinder cylinder 10. The annular pipe cavity C is formed based on the structure of the oil cylinder cylinder 10 itself, and there is no need for long oil pipe communication between the oil tank cylinder 60 and the oil cylinder 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 small volume. The oil supplementing and pressurizing response of the oil cylinder cylinder 10 is more rapid.

[0024] Further, the output end of the communication hole 31 communicates to the gap between the peripheral surface of the plunger 21 and the cylinder port of the oil cylinder cylinder 10. The gap forms an oil inlet channel of the oil cylinder cylinder 10, which on the one hand does not need to process an oil inlet hole on the cylinder body of the oil cylinder cylinder 10, ensuring the structural strength of the cylinder body of the oil cylinder cylinder 10, and on the other hand does not need to set a pipeline, and the structure is 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, and the structure of the valve body itself belongs to the prior art, which will not be described in detail here. In order to more clearly understand the oil flow between the pump body and the actuator, the basic control idea of the oil outlet control valve 80 is described here: the pressure oil discharged from the pressure oil discharge hole 41 enters the oil inlet P of the oil outlet control valve 80, and the oil outlet control valve 80 controls the pressure oil to be delivered to the actuator through the first working port A or the second working port B. When the first working port A sends oil to the actuator, the actuator will also return oil to the pump body through the second working port B (the oil inlet and outlet actions of the actuator can refer to the oil inlet and outlet actions of the traditional oil cylinder during operation). Conversely, when the second working port B sends oil to the actuator, the first working port A returns oil at the same time. Among them, whether it is the first working port A or the second working port B, the oil returned by the actuator will be discharged from the oil return port T of the oil outlet control valve 80, and then further discharged into the annular cavity C through the oil return hole 43 on the cylinder cover 40 and the pipe O for subsequent use of the pump body to increase the pressure, so that the actuator and the pump body form a circulating path of oil through the oil outlet control valve 80, and there is no need to supplement oil through the oil supplement tank 90.

[0030] In combination Figure 5 With Figure 6 As shown in the figure, the cover body of the cylinder cover 40 is provided with a first oil channel 44a and a second oil channel 44b which are in communication with each other, and the input ends of the first oil channel 44a and the second oil channel 44b are in communication with the output end of the second one-way valve 411, the output end of the first oil channel 44a is in communication with the accumulator 70, and the output end of the second oil channel 44b is in communication with the oil inlet P of the oil outlet control valve 80.

[0031] The common oil channel in the accumulator 70 is specifically described in this scheme. The first oil channel 44a serves as both an oil inlet channel and an oil outlet channel of the accumulator 70. In the state that the oil outlet control valve 80 is not opened, the reciprocating movement of the plunger 21 drives the oil cylinder barrel 10 to intake and discharge oil, thereby charging the accumulator 70, that is, the pressure oil enters the accumulator 70 through the first oil channel 44a. When the oil outlet control valve 80 is opened, the pressure oil in the accumulator 70 is discharged through the first oil channel 44a and enters the oil outlet control valve 80 through the second oil channel 44b in communication therewith, thereby supplying oil to the actuator.

[0032] Further, the cover body of the cylinder cover 40 is provided with a third oil channel 44c and an oil discharge channel 44d, the third oil channel 44c is in communication with the output end of the second one-way valve 411, and the oil discharge channel 44d is in communication with the annular cavity C. The cylinder cover 40 is provided with a pressure relief valve 100, and when the pressure relief valve 100 is opened / closed, the third oil channel 44c and the oil discharge channel 44d are in communication / blocked.

[0033] In the scheme, since the third oil passage 44c is communicated with the output end of the second check valve 411, the third oil passage 44c is also communicated with the first oil passage 44a and the second oil passage 44b. When maintenance of the pump body is needed, the pressure relief valve 100 is opened to communicate the third oil passage 44c with the oil discharge passage 44d, so that the pressure in the oil passages in the accumulator 70 and the cylinder head 40 can be released, facilitating maintenance.

[0034] As a preferred scheme, in order to monitor the pressure in the oil passages in the cylinder head 40, a pressure gauge 110 is arranged on the cylinder head 40 to monitor the pressure in the third oil passage 44c. When the pressure shown by the pressure gauge 110 is not up to standard, the oil passages in the cylinder head 40 and the accumulator 70 can be pressurized by reciprocating the plunger 21. Of course, the pressure relief valve 100 can also be used to determine whether the pressure in the pump body is completely released before maintenance of the pump body is performed, ensuring the safety of the operation.

[0035] As a preferred scheme, in order to facilitate disassembly and fixation of the second check valve 411, the pressure oil discharge hole 41 is a stepped through hole with a small inner diameter and a large outer diameter, and penetrates the inner and outer end faces of the cylinder head 40. A plug 412 is arranged in the outer hole end of the pressure oil discharge hole 41, and the inner end of the plug 412 is clamped on the opposite end face of the second check valve 411. When the second check valve 411 needs to be disassembled, the plug 412 is removed, and the second check valve 411 can be taken out from the large-diameter end of the pressure oil discharge hole 41. Conversely, the second check valve 411 is put into the large-diameter end of the pressure oil discharge hole 41, and the plug 412 is limited by the stepped face of the pressure oil discharge hole 41, so that the second check valve 411 is fixed.

[0036] Further, the plug 412 is tubular as a whole, and the tubular cavity constitutes the first oil passage 44a. The inner end of the plug 412 is communicated with the output end of the second check valve 411, and the outer end of the plug 412 is communicated with the accumulator 70. In the scheme, the plug 412 serves as a limiting piece for fixing the second check valve 411 and a connecting piece between the accumulator 70 and the cylinder head 40, which improves the integration of the accumulator 70 and the cylinder head 40, and helps to reduce the number of oil passages arranged in the cylinder head 40 and the manufacturing process 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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