Leak-proof automatic reciprocating supercharger

Abstract

The invention discloses an anti-leakage automatic reciprocating supercharger which comprises a valve body, a piston cavity, a liquid return channel and a liquid inlet channel. The piston is tightly attached to the valve body, is arranged in the piston cavity and can move in the axial direction; the piston cavity is divided into an oil inlet cavity communicated with the liquid inlet channel, an oil return cavity communicated with the liquid return channel and an oil outlet cavity; the round valve block is tightly attached to the interior of the valve body and is close to the oil outlet cavity; the circular valve block is provided with an annular oil inlet cavity, an annular oil control cavity and a second oil return cavity which are communicated with one another; the annular oil inlet cavity is communicated with the liquid inlet channel; the plungers are respectively arranged in the annular oil inlet cavity and the annular oil control cavity; the sliding block is located in the second oil return cavity and is tightly attached to the plunger; the sliding block is connected with the piston and provided with a channel assembly so as to communicate the annular oil inlet cavity with the annular control oil cavity or communicate the annular control oil cavity with the second oil return cavity when the sliding block is driven by the piston to move. And the hydraulic control unit is arranged in the valve body and is used for communicating the oil outlet cavity with the liquid inlet channel or communicating the oil outlet cavity with the oil return cavity so as to perform piston reversing.

Description

Technical Field

[0001] The present invention relates to the technical field of superchargers, and particularly to an anti-leakage automatic reciprocating supercharger. Background Art

[0002] In the field of automatic reciprocating supercharging, a supercharger is a key supercharging component widely used in industrial hydraulic systems, test devices, and gas-liquid conversion equipment. Its function is to boost low-pressure fluid to a higher pressure level through mechanical compression. The structure of existing automatic reciprocating superchargers usually consists of a large piston, a small piston, an automatic reversing valve, an inlet check valve, and an outlet check valve, etc. Among them, the large piston and the small piston generate high-pressure output by using differential area action and low-pressure drive to achieve energy conversion; the automatic reversing valve is used to control the flow direction of the driving gas or liquid, thereby realizing the automatic reciprocating motion of the piston; the check valve is used to control the fluid inlet and outlet to ensure the unidirectionality of pressure transmission and the stability of the system.

[0003] In the prior art, the large and small piston assemblies and the automatic reversing valve generally adopt a spool valve structure. In this structure, the piston and the cylinder block, and the spool and the valve body of the reversing valve are usually in clearance fit to ensure smooth sliding. However, while the clearance fit brings movement flexibility, it also inevitably brings the problem of poor sealing. During the actual operation of the supercharger, due to the large pressure difference between the high-pressure and low-pressure chambers, the piston clearance and the internal clearance of the reversing valve often become channels for high-pressure fluid to leak to the low-pressure side. This kind of leakage not only reduces the system efficiency and compression ratio, but also may cause problems such as insensitive commutation and unstable piston operation, thus affecting the continuous and stable operation of the supercharger. Especially in a long-term pressure-holding system that uses a low-pressure accumulator for re-supercharging, leakage will cause the pressure of the accumulator to drop, resulting in the inability to hold pressure.

[0004] Therefore, the prior art still needs to be improved and developed. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to provide an anti-leakage automatic reciprocating supercharger aiming at the above-mentioned defects of the prior art, so as to solve the technical problem of high-pressure and low-pressure leakage inside the supercharger in the prior art.

[0006] The technical solution adopted by the present invention to solve the technical problem is as follows:

[0007] An anti-leakage automatic reciprocating supercharger includes a valve body, in which a piston chamber, a liquid return channel, and a liquid inlet channel are provided. It further includes:

[0008] A piston is arranged in the piston cavity in close contact with the inner wall of the valve body and can reciprocate in the axial direction; the piston divides the piston cavity into an oil inlet cavity, an oil return cavity and an oil outlet cavity in the axial direction, the oil inlet cavity is communicated with the liquid inlet passage, and the oil return cavity is communicated with the liquid return passage;

[0009] A circular valve block is tightly arranged in the valve body and close to the oil outlet chamber; the circular valve block is provided with an annular oil inlet chamber, an annular control oil chamber and a second oil return chamber which are interconnected; the second oil return chamber axially passes through the center of the circular valve block, and the annular oil inlet chamber is also connected to the liquid inlet passage;

[0010] A plunger is respectively arranged in the annular oil inlet chamber and the annular control oil chamber and has a central hole;

[0011] A slider is located in the second oil return chamber and is tightly fitted with the plunger; the slider is connected to the piston, and a channel assembly is provided on the slider to connect the annular oil inlet chamber with the annular control oil chamber, or connect the annular control oil chamber with the second oil return chamber when the slider reciprocates relative to the plunger under the drive of the piston;

[0012] A hydraulic control unit is arranged in the valve body and located on the side of the circular valve block away from the piston; the hydraulic control unit is used to connect the oil outlet chamber with the liquid inlet channel, or connect the oil outlet chamber with the oil return chamber to perform reversal of the piston.

[0013] The anti-leakage automatic reciprocating supercharger, wherein the piston comprises:

[0014] A small piston is close to the oil inlet chamber and fits tightly against the inner wall of the valve body;

[0015] The large piston is nested outside the small piston and is located on the axial side of the small piston away from the oil inlet chamber; the large piston is tightly fitted with the inner wall of the valve body.

[0016] The anti-leakage automatic reciprocating supercharger further comprises:

[0017] A pull rod sleeve is arranged in the valve body; the first end of the pull rod sleeve is located on the side of the large piston away from the small piston, and is surrounded by the large piston to form the oil outlet cavity; the second end of the pull rod sleeve is inserted into the large piston, and is slidably matched with the large piston;

[0018] A connecting component has one end located in the large piston and the other end extending into the second oil return chamber after passing through the pull rod sleeve and assembled with the slider to drive the slider to reciprocate under the drive of the piston.

[0019] For the leak-proof automatic reciprocating supercharger, the radial cross-sectional area of the large piston minus the radial cross-sectional area of the pull rod sleeve is greater than the radial cross-sectional area of the small piston.

[0020] For the leak-proof automatic reciprocating supercharger, the connection assembly includes:

[0021] A pull rod axially penetrating through the pull rod sleeve;

[0022] A limiting portion located inside the large piston and sleeved on the end of the pull rod; at least part of the limiting portion coincides with the second end of the pull rod sleeve;

[0023] A hook located in the second oil return chamber and connected to the end of the pull rod away from the limiting portion; a receiving position is provided on the hook, and the receiving position has an opening; the slider is arranged in the receiving position, and the plunger is in close fit with the slider through the opening.

[0024] For the leak-proof automatic reciprocating supercharger, the channel assembly includes:

[0025] A first channel having a first opening and a second opening; both the first opening and the second opening are located on the outer circumferential surface of the slider and are used to communicate with the annular oil inlet chamber and the annular control oil chamber respectively;

[0026] A second channel having a third opening and a fourth opening; the third opening is located on the outer circumferential surface of the slider and is used to communicate with the annular control oil chamber; the fourth opening is located on the axial end face of the slider on the side away from the piston and is used to communicate with the second oil return chamber.

[0027] For the leak-proof automatic reciprocating supercharger, the hydraulic control unit includes:

[0028] A hydraulic control push rod connected to the round valve block; a second oil inlet chamber communicating with the liquid inlet channel is provided at the axial end of the hydraulic control push rod on the side away from the round valve block;

[0029] A sphere coaxially arranged with the hydraulic control push rod and close to the second oil inlet chamber;

[0030] A hydraulic control valve assembly sleeved on the hydraulic control push rod and the sphere;

[0031] A second oil outlet chamber connected to the oil outlet chamber is provided between the hydraulic control valve assembly and the hydraulic control push rod, a third oil return chamber connected to the return liquid channel is provided between the hydraulic control valve assembly and the ball, and a third oil inlet chamber connected to the liquid inlet channel is provided on the axial side of the hydraulic control valve assembly away from the circular valve block; the hydraulic control valve assembly can reciprocate along the axial direction and drive the ball to cover the opening of the second oil inlet chamber to connect the second oil outlet chamber with the third oil return chamber, or drive the ball to open the opening of the second oil inlet chamber to connect the second oil inlet chamber with the second oil outlet chamber.

[0032] The anti-leakage automatic reciprocating booster, wherein the hydraulic control valve assembly comprises:

[0033] A hydraulically controlled valve sleeve is sleeved outside the hydraulically controlled ejector rod and can reciprocate along the axial direction; a through hole is provided on the hydraulically controlled valve sleeve, the through hole is communicated with the opening of the second oil inlet chamber, and the diameter of the through hole is smaller than the diameter of the sphere; the second oil outlet chamber is located between the inner wall of the hydraulically controlled valve sleeve and the hydraulically controlled ejector rod;

[0034] A valve sleeve is arranged at one end of the hydraulic control valve sleeve away from the circular valve block; the third oil return chamber is located in the valve sleeve, and the ball is located in the third oil return chamber;

[0035] The valve core is arranged in the valve sleeve and is located on the side of the ball away from the hydraulic control push rod to drive the ball to cover the opening of the second oil inlet chamber.

[0036] The anti-leakage automatic reciprocating supercharger, wherein the valve sleeve is provided with a groove, the valve body is provided with a fourth oil return chamber, and the fourth oil return chamber is communicated with the oil return chamber; the hydraulically controlled push rod and the hydraulically controlled valve sleeve are both located in the fourth oil return chamber; the groove is communicated with the third oil return chamber and the fourth oil return chamber respectively.

[0037] The anti-leakage automatic reciprocating supercharger, wherein the difference between the radial cross-sectional area of the hydraulically controlled valve sleeve and the radial cross-sectional area of the portion of the hydraulically controlled push rod disposed inside the hydraulically controlled valve sleeve is greater than the radial cross-sectional area of the valve sleeve.

[0038] Beneficial effect: In the present application, the hydraulic control unit is used to enable the piston to achieve reversal and pressurization. At the same time, the close fit between the piston and the valve body, the sliding fit between the slider and the plunger, and the pressure of the annular oil inlet chamber and the annular control oil chamber on the plunger are utilized, so that high and low pressure leakage will not occur inside the valve body due to the existence of clearance fit, thereby avoiding the occurrence of problems such as insensitive reversing and unstable piston operation caused by high and low pressure leakage. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Figure 1It is a schematic diagram of the overall sectional structure of the anti-leakage automatic reciprocating supercharger described in this application;

[0040] Figure 2 It is a reference diagram of the usage state of the anti-leakage automatic reciprocating supercharger when the opening of the second oil inlet chamber described in this application is blocked by the sphere;

[0041] Figure 3 It is a reference diagram of the usage state of the anti-leakage automatic reciprocating supercharger when the opening of the second oil inlet chamber described in this application is opened;

[0042] Figure 4 It is a schematic diagram of the exploded structure of the piston and the pull rod described in this application;

[0043] Figure 5 It is a schematic diagram of the assembly structure of the pull rod, the hook and the slider described in this application;

[0044] Figure 6 It is a schematic diagram of the structure of the valve sleeve described in this application;

[0045] Figure 7 Schematic diagram of the exploded structure of the anti-leakage automatic reciprocating supercharger described in this application. Detailed implementation manners

[0046] To make the objectives, technical solutions and advantages of the present invention clearer and more definite, the following further describes the present invention in detail with reference to the accompanying drawings and by way of examples. It should be understood that the specific examples described herein are only used to explain the present invention and are not used to limit the present invention.

[0047] The present invention provides an anti-leakage automatic reciprocating supercharger, as shown in Figure 1As shown in the figure, the leak-proof automatic reciprocating supercharger includes: a valve body 1, a piston 2, a circular valve block 3, a plunger 4, a slider 5, and a hydraulic control unit 6; a piston chamber, a liquid return passage, and a liquid inlet passage are provided in the valve body 1, the piston 2 is disposed in the piston chamber in close fit with the inner wall of the valve body 1, and can reciprocate axially; the piston 2 divides the piston chamber into an oil inlet chamber 7, an oil return chamber 8, and an oil outlet chamber 9 in sequence along the axial direction, the oil inlet chamber 7 is communicated with the liquid inlet passage, and the oil return chamber 8 is communicated with the liquid return passage; the circular valve block 3 is disposed in the valve body 1 in close fit and is close to the oil outlet chamber 9; an annular oil inlet chamber 11, an annular control oil chamber 12, and a second oil return chamber 10 which are communicated with each other are provided on the circular valve block 3; the second oil return chamber 10 axially penetrates through the center of the circular valve block 3, and the annular oil inlet chamber 11 is also communicated with the liquid inlet passage; the plunger 4 is respectively disposed in the annular oil inlet chamber 11 and the annular control oil chamber 12 and has a central hole 41; the slider 5 is located in the second oil return chamber 10 and is in close fit with the plunger 4; the slider 5 is connected to the piston 2, and a channel assembly 51 is provided on the slider 5 to communicate the annular oil inlet chamber 11 with the annular control oil chamber 12, or communicate the annular control oil chamber 12 with the second oil return chamber 10 when the slider 5 reciprocates relative to the plunger 4 driven by the piston 2; the hydraulic control unit 6 is disposed in the valve body 1 and is located on the side of the circular valve block 3 away from the piston 2; the hydraulic control unit 6 is used to communicate the oil outlet chamber 9 with the liquid inlet passage, or communicate the oil outlet chamber 9 with the oil return chamber 8 to perform commutation of the piston 2.

[0048] Specifically, the piston 2, the circular valve block 3, and the hydraulic control unit 6 are arranged in sequence along the axial direction and are coaxially disposed in the valve body 1; the cavity in the valve body 1 for accommodating the piston 2 is the piston chamber, and the piston chamber is divided by the piston 2 into an oil inlet chamber 7, an oil return chamber 8, and an oil outlet chamber 9; the oil inlet chamber 7, the oil return chamber 8, and the oil outlet chamber 9 are arranged in sequence along the axial direction, and the oil outlet chamber 9 is located on the side of the piston 2 close to the circular valve block 3, so that when the oil outlet chamber 9 is communicated with the oil return chamber 8, the side of the piston 2 close to the circular valve block 3 axially relieves pressure, and as the oil inlet chamber 7 intakes oil, the pressure on the side of the piston 2 axially away from the circular valve block 3 increases, and the piston 2 moves in the direction towards the circular valve block 3; when the oil outlet chamber 9 is communicated with the liquid inlet passage, the pressure on the side of the piston 2 axially close to the circular valve block 3 exceeds the pressure on the side of the oil inlet chamber 7, then the piston 2 moves in the direction away from the circular valve block 3, and thus the commutation of the piston 2 can be realized.

[0049] One axial end of the valve body 1 is provided with a liquid outlet 105, and the other end is respectively provided with a liquid return port 106 and a liquid inlet 107; the liquid outlet 105 is communicated with the oil inlet cavity 7 through a one-way liquid outlet valve 108, the liquid return port 106 is communicated with the liquid return channel, and the liquid inlet 107 is communicated with the liquid inlet channel. Then, when the piston 2 moves away from the direction of the circular valve block 3, that is, when the piston 2 moves in the direction of the oil inlet cavity 7 for commutation, pressure boost can be achieved.

[0050] It should be noted that since the outer circumferential surface of the piston 2 is in close contact with the inner wall of the valve body 1 instead of clearance fit, when the piston 2 commutes, leakage of high and low pressures is avoided, and sealing between the outer circumferential surface of the piston 2 and the inner wall of the valve body 1 is achieved.

[0051] The position of the circular valve block 3 in the valve body 1 remains fixed and is located on one side of the piston 2 axially close to the oil outlet cavity 9; the annular oil inlet cavity 11 and the annular control oil cavity 12 are respectively arranged on the outer circumferential surface of the circular valve block 3; there are 4 plungers 4, and one end of the plunger 4 is located in the second oil return cavity 10 and is pressed against the slider 5. Two of the plungers 4 correspond to the annular oil inlet cavity 11, and the end of the plunger 4 facing away from the slider 5 is placed in the annular oil inlet cavity 11, and the slider 5 is communicated with the annular oil inlet cavity 11 through the central hole 41 of the plunger 4; the other two plungers 4 correspond to the annular control oil cavity 12, and the end of the plunger 4 facing away from the slider 5 is placed in the annular control oil cavity 12, and the slider 5 is communicated with the annular control oil cavity 12 through the central hole 41 of the plunger 4.

[0052] Since the slider 5 is connected to the piston 2, when the piston 2 commutes and moves, the slider 5 will also generate a commutation movement relative to the plunger 4; then, driven by the piston 2, when the slider 5 reciprocates axially, two states can be achieved: one is that the slider 5 can move to the channel assembly 51 to communicate the annular oil inlet cavity 11 with the annular control oil cavity 12, and the other is that the slider 5 can move to the channel assembly 51 to communicate the annular control oil cavity 12 with the second oil return cavity 10.

[0053] The liquid control unit 6 is used to communicate the oil outlet cavity 9 with the liquid inlet channel when the annular oil inlet cavity 11 is communicated with the annular control oil cavity 12 through the channel assembly 51, so that the piston 2 can commute towards the side of the circular valve block 3; the liquid control unit 6 is also used to communicate the oil outlet cavity 9 with the oil return cavity 8 when the annular control oil cavity 12 is communicated with the second oil return cavity 10 through the channel assembly 51, so that the piston 2 can commute towards the side away from the circular valve block 3.

[0054] When the slider 5 and the plunger 4 in the present application are tightly fitted and slidably matched, since the inner side of the plunger 4 presses the slider 5 and is in the environment of the second oil return chamber 10, and the outer side of the plunger 4 is the annular control oil chamber 12 or the annular oil inlet chamber 11, as the pressure increases, the slider 5 and the plunger 4 are pressed tighter and tighter, achieving zero leakage between the circular valve block 3 and the valve body 1, and realizing a long-term pressure maintaining system using a low-pressure accumulator for re-pressurization to avoid a drop in accumulator pressure due to leakage.

[0055] Therefore, in the present application, the hydraulic control unit 6 is used to enable the piston 2 to achieve reversing and pressurization. At the same time, the close fit between the piston 2 and the valve body 1, the sliding fit between the slider 5 and the plunger 4, and the pressure of the annular oil inlet chamber 11 and the annular control oil chamber 12 on the plunger 4 are utilized, so that the inside of the valve body 1 will not produce high and low pressure leakage due to the existence of clearance fit, thereby avoiding the occurrence of problems such as insensitive reversing and unstable piston operation caused by high and low pressure leakage, and significantly improving the sealing reliability and system operation stability.

[0056] like Figure 1 and Figure 7 As shown, the valve body 1 includes: a high-pressure valve body 101, a low-pressure valve body 102, a reversing valve body 103 and an oil inlet valve body 104; the high-pressure valve body 101, the low-pressure valve body 102, the reversing valve body 103 and the oil inlet valve body 104 are coaxially arranged in sequence along the axial direction; the piston 2 is partially located in the high-pressure valve body 101 and partially located in the low-pressure valve body 102; the round valve block 3 is located in the reversing valve body 103; the hydraulic control unit 6 is partially located in the reversing valve body 103 and partially located in the oil inlet valve body 104. The liquid outlet 105 is arranged on the axial end surface of the high-pressure valve body 101 on the side away from the low-pressure valve body 102; the liquid inlet 107 and the liquid return port 106 are both arranged on the axial end surface of the oil inlet valve body 104 on the side away from the reversing valve body 103.

[0057] like Figure 1 , Figure 4 and Figure 7 As shown, the piston 2 includes a large piston 201 and a small piston 202; the small piston 202 is close to the oil inlet chamber 7 and fits tightly against the inner wall of the valve body 1; the large piston 201 is nested outside the small piston 202 and is located on the axial side of the small piston 202 away from the oil inlet chamber 7; the large piston 201 fits tightly against the inner wall of the valve body 1.

[0058] Specifically, the outer diameter of the small piston 202 is smaller than that of the large piston 201, and a part of the small piston 202 is placed inside the large piston 201, so that the small piston 202 and the large piston 201 are arranged in a nested manner. Then, the large piston 201 and the small piston 202 can form a piston assembly to perform commutation and pressure boosting. An oil inlet cavity 7 is provided at the axial end of the high-pressure valve body 101 close to the low-pressure valve body 102. The opening of the oil inlet cavity 7 faces the low-pressure valve body 102 and is used to accommodate the small piston 202. Moreover, the outer circumferential surface of the small piston 202 is in close fit with the inner wall of the oil inlet cavity 7. The large piston 201, the oil return cavity 8, and the oil outlet cavity 9 are all located inside the low-pressure valve body 102, and the outer circumferential surface of the large piston 201 is in close fit with the inner wall of the low-pressure valve body 102.

[0059] As Figure 4 shown, a first abutting step 203 is provided at the axial end of the large piston 201. The axial end of the small piston 202 away from the oil inlet cavity 7 is located inside the first abutting step 203. Then, when the oil outlet cavity 9 is communicated with the oil return cavity 8, under the pressure of the oil inlet cavity 7, the small piston 202 can abut against the large piston 201 to move and commutate synchronously towards the circular valve block 3. When the oil outlet cavity 9 is communicated with the oil inlet cavity 7, under the pressure of the oil outlet cavity 9, the large piston 201 can abut against the small piston 202 to move and commutate synchronously in a direction away from the circular valve block 3.

[0060] The leak-proof automatic reciprocating supercharger further includes a pull rod sleeve 19 and a connecting assembly. The pull rod sleeve 19 is arranged inside the valve body 1. The first end of the pull rod sleeve 19 is located on the side of the large piston 201 away from the small piston 202, and a surrounding forms the oil outlet cavity 9 with the large piston 201. The second end of the pull rod sleeve 19 is inserted into the large piston 201 and is in sliding fit with the large piston 201. One end of the connecting assembly is located inside the large piston 201, and the other end of the connecting assembly passes through the pull rod sleeve 19 and extends into the second oil return cavity 10, and is assembled with the slider 5 to drive the slider 5 to reciprocate under the drive of the piston 2.

[0061] Specifically, the position of the pull rod sleeve 19 inside the valve body 1 is fixed. One end of the pull rod sleeve 19 is located inside the low-pressure valve body 102 and is inserted into the large piston 201. The other end of the pull rod sleeve 19 extends into the commutation valve body 103 and is in contact with the circular valve block 3. When the large piston 201 moves and commutates, the large piston 201 can reciprocally slide relative to the pull rod sleeve 19.

[0062] The connecting assembly is used to connect the large piston 201 with the slider 5, and drives the slider 5 to move when the piston 2 moves, so as to adjust the communication relationship between the channel assembly 51 and the annular oil inlet chamber 11, the annular control oil chamber 12 and the second oil return chamber 10. The tie rod sleeve 19 includes a tie rod sleeve body 191 and a vertical portion 192. The tie rod sleeve body 191 is arranged along the axial extension of the valve body 1. The vertical portion 192 is integrally formed with the tie rod sleeve body 191 and is perpendicular to the tie rod sleeve body 191, so that the tie rod sleeve 19 forms a T-shaped structure. The tie rod sleeve body 191 is inserted into the large piston 201, and the space between the vertical portion 192 and the large piston 201 forms the oil outlet chamber 9. When the piston 2 moves toward the circular valve block 3, the volume of the oil outlet chamber 9 decreases; when the piston 2 moves away from the circular valve block 3, the volume of the oil outlet chamber 9 increases. The space between the large piston 201 and the high-pressure valve body 101 forms the oil return chamber 8. When the piston 2 moves toward the circular valve block 3, the volumes of the oil return chamber 8 and the oil inlet chamber 7 increase; when the piston 2 moves away from the circular valve block 3, the volumes of the oil return chamber 8 and the oil inlet chamber 7 decrease.

[0063] like Figure 4 and Figure 5 As shown, the connecting assembly includes a pull rod 20, a limiting portion 22 and a hook 21; the pull rod 20 axially penetrates the pull rod sleeve 19; the limiting portion 22 is located in the large piston 201 and is sleeved on the end of the pull rod 20; the limiting portion 22 at least partially overlaps with the second end of the pull rod sleeve 19; the hook 21 is located in the second oil return chamber 10 and is connected to the end of the pull rod 20 away from the limiting portion 22; a receiving position is provided on the hook 21, and the receiving position has an opening; the slider 5 is provided in the receiving position, and the plunger 4 is tightly fitted with the slider 5 through the opening of the receiving position.

[0064] Specifically, the pull rod 20 and the pull rod sleeve 19 are coaxially arranged; the pull rod 20 is respectively engaged with the small piston 202, the large piston 201 and the pull rod sleeve 19 through the limiting portion 22. A second abutting step 204 engaged with the limiting portion 22 is provided on the large piston 201; the outer diameter of the limiting portion 22 is larger than the outer diameter of the pull rod sleeve body 191, so that the outer edge of the limiting portion 22 can extend beyond the pull rod sleeve body 191 to be engaged with the second abutting step 204. When the large piston 201 moves to contact the vertical portion 192, the second abutting step 204 is away from the limiting portion 22, and the second abutting step 204 is located on the side of the limiting portion 22 close to the circular valve block 3, and the small piston 202 abuts against the limiting portion 22; when the small piston 202 moves away from the circular valve block 3 to the limit, the limiting portion 22 is located within the second abutting step 204, and the small piston 202 is away from the limiting portion 22.

[0065] Through the limiting portion 22, the pull rod 20 can realize the influence of the movement of the piston 2 on the position of the pull rod 20. When the piston 2 moves from the extreme position away from the circular valve block 3 towards the circular valve block 3 at the initial stage, the small piston 202 does not contact the limiting portion 22, then the pull rod 20 will not push the slider 5 to move, and only when the large piston 201 moves towards the circular valve block 3 to the last position (that is, when the small piston 202 abuts against the limiting portion 22), the small piston 202 can push the pull rod 20 to continue moving towards the circular valve block 3 until the limiting portion 22 abuts against the pull rod sleeve 19 and the piston 2 stops moving, realizing the pushing of the slider 5. When the piston 2 moves away from the circular valve block 3 from the extreme position close to the circular valve block 3 at the initial stage, the second abutting step 204 and the limiting portion 22 are separated from each other, and the large piston 201 cannot exert a pulling effect on the pull rod 20, then the slider 5 remains stationary; only when the large piston 201 moves away from the circular valve block 3 to the last position (that is, when the limiting portion 22 is placed within the second abutting step 204), the large piston 201 pushes the pull rod 20 to continue moving away from the circular valve block 3 through the limiting portion 22, thereby realizing the pulling of the slider 5 until the large piston 201 abuts against the axial end face of the high-pressure valve body 101 and the piston 2 stops moving.

[0066] It can be seen that in the present application, both the pushing and pulling of the pull rod 20 on the slider 5 need to wait until the large piston 201 moves to the last position to be realized, reducing the friction of the slider 5, thereby prolonging the service life of the slider 5.

[0067] Such as Figure 2 、 Figure 3 and Figure 4As shown, the channel assembly 51 includes a first channel 511 and a second channel 512; the first channel 511 has a first opening and a second opening; the first opening and the second opening are both located on the outer circumferential surface of the slider 5, and are used to communicate with the annular oil inlet chamber 11 and the annular control oil chamber 12 respectively; the second channel 512 has a third opening and a fourth opening; the third opening is located on the outer circumferential surface of the slider 5, and is used to communicate with the annular control oil chamber 12; the fourth opening is located on the axial end face of the slider 5 away from the piston 2, and is used to communicate with the second oil return chamber 10.

[0068] Specifically, the two openings of the first channel 511 are used to respectively connect the annular oil inlet chamber 11 and the annular control oil chamber 12; since a center hole 41 is provided on the plunger 4, for the plunger 4 corresponding to the annular oil inlet chamber 11: one end of the plunger 4 fits the slider 5, and the other end extends into the annular oil inlet chamber 11, and when the slider 5 moves to the point where the first opening corresponds to the center hole 41, the first channel 511 can be connected to the annular oil inlet chamber 11. Similarly, for the plunger 4 corresponding to the annular control oil chamber 12, when the slider 5 moves to the point where the first opening corresponds to the plunger 4 in the annular oil inlet chamber 11, the second opening can correspond to the plunger 4 in the annular control oil chamber 12, and the first channel 511 can be connected to the annular control oil chamber 12, thereby realizing the connection between the annular oil inlet chamber 11 and the annular control oil chamber 12 by the first channel 511 (such as Figure 3 shown).

[0069] It is understandable that the present application does not impose any specific restrictions on the shape of the first channel 511, and the first channel 511 may be in a V-shape, a π-shape, or the like, as long as the first opening and the second opening are connected. Figure 7 As shown, the circular valve block 3 is provided with mounting holes 40 for the plungers 4, and the mounting holes 40 are arranged along the radial extension of the circular valve block 3; two of the mounting holes are respectively connected with the annular oil inlet chamber 11 and the second oil return chamber 10 to install the two plungers 4 corresponding to the annular oil inlet chamber 11; the other two mounting holes are respectively connected with the annular control oil chamber 12 and the second oil return chamber 10 to install the two plungers 4 corresponding to the annular control oil chamber 12.

[0070] The second channel 512 is an L-shaped channel. The fourth opening is located on the axial end face of the slider 5, and there is a gap between the axial end face of the slider 5 where the fourth opening is provided and the hook 21 to ensure that the fourth opening can communicate with the second oil return cavity 10. In this way, when the slider 5 moves to a position where the third opening corresponds to the plunger 4 in the annular control oil cavity 12, the second channel 512 can communicate the annular control oil cavity 12 with the second oil return cavity 10 (as Figure 2 shown).

[0071] As Figure 1 shown, the hydraulic control unit 6 includes a hydraulic control ejector rod 61, a sphere 62 and a hydraulic control valve assembly 63; the hydraulic control ejector rod 61 is connected to the circular valve block 3; a second oil inlet cavity 13 communicating with the liquid inlet passage is provided at the axial end of the hydraulic control ejector rod 61 on the side away from the circular valve block 3; the sphere 62 is coaxially arranged with the hydraulic control ejector rod 61 and is close to the second oil inlet cavity 13; the hydraulic control valve assembly 63 is sleeved outside the hydraulic control ejector rod 61 and the sphere 62; there is a second oil outlet cavity 14 communicating with the oil outlet cavity 9 between the hydraulic control valve assembly 63 and the hydraulic control ejector rod 61, and there is a third oil return cavity 16 communicating with the liquid return passage between the hydraulic control valve assembly 63 and the sphere 62; a third oil inlet cavity 17 communicating with the liquid inlet passage is provided on the axial side of the hydraulic control valve assembly 63 away from the circular valve block 3; the hydraulic control valve assembly 63 can reciprocate axially and drive the sphere 62 to block the opening of the second oil inlet cavity 13 (as Figure 2 shown) to separate the second oil outlet cavity 14 from the third oil return cavity 16, or drive the sphere 62 to open the opening of the second oil inlet cavity 13 (as Figure 3 shown) to communicate the second oil inlet cavity 13 with the second oil outlet cavity 14.

[0072] Specifically, the liquid outlet 105 is connected to the oil inlet chamber 7 through a liquid outlet check valve 108, and the liquid inlet 107 is connected to the third oil inlet chamber 17, the annular oil inlet chamber 11 and the oil inlet chamber 7 in sequence; a liquid inlet check valve 109 is also provided between the oil inlet chamber 7 and the annular oil inlet chamber 11. If the difference between the radial cross-sectional area of the large piston 201 and the radial cross-sectional area of the tie rod sleeve 19 (the radial cross-sectional area of the tie rod sleeve body 191) is greater than the radial cross-sectional area of the small piston 202, when the large piston 201 moves away from the circular valve block 3, the liquid inlet check valve 109 is closed, the liquid in the oil inlet chamber 7 is compressed, the pressure is increased, and the pressurization is achieved. The reversing valve body 103 has a fourth oil return chamber 18, and the fourth oil return chamber 18 is located between the round valve block 3 and the oil inlet valve body 104; the hydraulic control push rod 61 is located in the fourth oil return chamber 18; the hydraulic control valve assembly 63 is partially located in the fourth oil return chamber 18, and partially extends into the oil inlet valve body 104, and is surrounded by the oil inlet valve body 104 to form the third oil inlet chamber 17; the oil return chamber 8 and the fourth oil return chamber 18 are both connected to the return liquid port 106.

[0073] The hydraulic control valve assembly 63 includes: a hydraulic control valve sleeve 631, a valve sleeve 632 and a valve core 633; the hydraulic control valve sleeve 631 is sleeved outside the hydraulic control push rod 61 and can reciprocate along the axial direction; a through hole is provided on the hydraulic control valve sleeve 631, the through hole is connected with the opening of the second oil inlet chamber 13, and the diameter of the through hole is smaller than the diameter of the ball 62, so that when the hydraulic control valve sleeve 631 moves away from the hydraulic control push rod 61, the ball 62 can be pushed away from the hydraulic control push rod 61, thereby opening the opening of the second oil inlet chamber 13. The second oil outlet chamber 14 is located between the inner wall of the hydraulic control valve sleeve 631 and the hydraulic control push rod 61; the valve sleeve 632 is provided at one end of the hydraulic control valve sleeve 631 away from the circular valve block 3; the third oil return chamber 16 is located in the valve sleeve 632, and the ball 62 is located in the third oil return chamber 16. The valve core 633 is arranged in the valve sleeve 632 and is located on the side of the ball 62 away from the hydraulic control push rod 61. Therefore, when the hydraulic control valve assembly 63 moves toward the hydraulic control push rod 61, the valve core 633 can drive the ball 62 to move toward the hydraulic control push rod 61, thereby blocking the opening of the second oil inlet chamber 13.

[0074] Specifically, the hydraulic control push rod 61 has a T-shaped structure and is arranged in the opposite direction to the T-shaped structure of the pull rod sleeve 19. One end of the hydraulic control push rod 61 is inserted into the hydraulic control valve sleeve 631, and the other end is used to limit the hydraulic control valve sleeve 631. The second control oil chamber 15 is located between the axially outer end face of the hydraulic control valve sleeve 631 close to the circular valve block 3 and the hydraulic control push rod 61. The outer circumferential surface of the part of the hydraulic control push rod 61 inserted into the hydraulic control valve sleeve 631 is in close contact with the inner wall of the hydraulic control valve sleeve 631, so that a second oil return chamber 10 is formed between the axially inner end face of the hydraulic control valve sleeve 631 close to the circular valve block 3 and the hydraulic control push rod 61. A nut 23 is also arranged in the fourth oil return chamber 18, and the nut 23 is in threaded cooperation with the hydraulic control push rod 61 and the hydraulic control valve sleeve 631 respectively.

[0075] The second control oil chamber 15 is communicated with the annular control oil chamber 12. When the slider 5 moves to a position where the annular control oil chamber 12 is communicated with the second oil return chamber 10, the second control oil chamber 15 discharges pressure to the liquid return port 106 through the annular control oil chamber 12 and the second oil return chamber 10 in sequence. The overall structure formed by the hydraulic control valve sleeve 631, the valve sleeve 632 and the valve core 633 moves towards the hydraulic control push rod 61, driving the sphere 62 to move until the sphere 62 contacts the hydraulic control push rod 61 and blocks the opening of the second oil inlet chamber 13. When the slider 5 moves to a position where the annular oil inlet chamber 11 is communicated with the annular control oil chamber 12, the annular oil inlet chamber 11 supplies oil to the second control oil chamber 15 through the annular control oil chamber 12. The overall structure formed by the hydraulic control valve sleeve 631, the valve sleeve 632 and the valve core 633 moves away from the hydraulic control push rod 61, and drives the sphere 62 to disengage from the opening of the second oil inlet chamber 13, thereby opening the opening of the second oil inlet chamber 13.

[0076] As Figure 6 and Figure 7 shown, a slot 634 is provided on the valve sleeve 632, a fourth oil return chamber 18 is provided in the valve body 1, and the fourth oil return chamber 18 is communicated with the oil return chamber 8. Both the hydraulic control push rod 61 and the hydraulic control valve sleeve 631 are located in the fourth oil return chamber 18. The slot 634 is communicated with the third oil return chamber 16 and the fourth oil return chamber 18 respectively, so as to realize the communication between the fourth oil return chamber 18 and the third oil return chamber 16.

[0077] It should be noted that the oil outlet cavity 9 is communicated with the second oil outlet cavity 14, and the oil return cavity 8, the second oil return cavity 10, the third oil return cavity 16 and the fourth oil return cavity 18 are all communicated with each other; the annular control oil cavity 12 is communicated with the second control oil cavity, and the oil inlet cavity 7, the annular oil inlet cavity 11, the second oil inlet cavity 13 and the third oil inlet cavity 17 are all communicated with each other. When the sphere 62 blocks the opening of the second oil inlet cavity 13, the second oil outlet cavity 14 can be communicated with the third oil return cavity 16, then the oil outlet cavity 9 is communicated with the oil return cavity 8 through the third oil return cavity 16 and is depressurized, and the piston 2 can move in the direction of the circular valve block 3 for commutation. When the sphere 62 opens the opening of the second oil inlet cavity 13, the second oil inlet cavity 13 can be communicated with the second oil outlet cavity 14, and the communication between the second oil outlet cavity 14 and the third oil return cavity 16 is cut off; then the oil outlet cavity 9 can be filled with oil through the second oil outlet cavity 14 and the second oil inlet cavity 13, so as to push the piston 2 to move in the direction away from the circular valve block 3 for commutation.

[0078] In this application, when the large piston 201 moves to the limit in the direction away from the circular valve block 3, the large piston 201 abuts against the axial end face of the high-pressure valve body 101, and through the cooperation of the second abutting step 204 and the pull rod 20, the slider 5 is pulled towards the piston 2 until the second channel 512 communicates the annular control oil cavity 12 with the second oil return cavity 10 respectively; as Figure 2 shown, under the communication action between the annular control oil cavity 12 and the second control oil cavity 15, the second control oil cavity 15 is depressurized to the oil return cavity 8 through the second oil return cavity 10, and the liquid control valve sleeve 631, the valve sleeve 632 and the valve core 633 are pushed towards the liquid control ejector rod 61 by the pressure of the third oil inlet cavity 17 until the sphere 62 blocks the opening of the second oil inlet cavity 13, the second oil outlet cavity 14 is communicated with the third oil return cavity 16, and the communication between the second oil inlet cavity 13 and the second oil outlet cavity 14 is cut off. At this time, the liquid control valve sleeve 631 obtains a new force in the direction of the liquid control ejector rod 61, so as to accelerate the movement towards the direction close to the liquid control ejector rod 61, realizing the accelerated closing of the opening of the second oil inlet cavity 13; then the oil outlet cavity 9 is communicated with the oil return cavity 8 through the third oil return cavity 16 and is depressurized, and the piston 2 can move in the direction of the circular valve block 3 for commutation.

[0079] When the large piston 201 moves towards the circular valve block 3 to the limit, the large piston 201 abuts against the pull rod sleeve 19, and the small piston 202 abuts against the pull rod 20, so that the pull rod 20 pushes the slider 5 to move towards the hydraulic control unit 6 until the first channel 511 connects the annular control oil chamber 12 and the annular oil inlet chamber 11 respectively; as Figure 3 shown, under the communication action between the second control oil chamber 15 and the annular control oil chamber 12, the second control oil chamber 15 is filled with oil through the annular oil inlet chamber 11, and the difference between the radial cross-sectional area of the hydraulic control valve sleeve 631 and the radial cross-sectional area of the part of the hydraulic control push rod 61 located inside the hydraulic control valve sleeve 631 is greater than the radial cross-sectional area of the valve sleeve 632, so that the hydraulic control valve sleeve 631, the valve sleeve 632 and the valve core 633 move away from the hydraulic control push rod 61 as a whole, and the hydraulic control valve sleeve 631 pushes the sphere 62 away from the hydraulic control push rod 61, thereby opening the opening of the second oil inlet chamber 13. When the sphere 62 opens the opening of the second oil inlet chamber 13, the second oil inlet chamber 13 can communicate with the second oil outlet chamber 14. At this time, the hydraulic control valve sleeve 631 obtains a new force to move away from the hydraulic control push rod 61, so as to accelerate the movement in the direction away from the hydraulic control push rod 61, realizing the accelerated opening of the opening of the second oil inlet chamber 13; then the oil outlet chamber 9 can be filled with oil through the second oil outlet chamber 14 and the second oil inlet chamber 13, thereby pushing the piston 2 to move in the reverse direction away from the circular valve block 3 to achieve pressure boosting.

[0080] It should be understood that the application of the present invention is not limited to the above examples. For those of ordinary skill in the art, improvements or transformations can be made according to the above description, and all these improvements and transformations should fall within the protection scope of the appended claims of the present invention.

Claims

1. An anti-leakage automatic reciprocating supercharger, which comprises a valve body, wherein a piston chamber, a liquid return channel and a liquid inlet channel are arranged in the valve body, and is characterized in that, It also includes: A piston is arranged in the piston cavity in close contact with the inner wall of the valve body and can reciprocate in the axial direction; the piston divides the piston cavity into an oil inlet cavity, an oil return cavity and an oil outlet cavity in the axial direction, the oil inlet cavity is communicated with the liquid inlet passage, and the oil return cavity is communicated with the liquid return passage; A circular valve block is tightly arranged in the valve body and close to the oil outlet chamber; the circular valve block is provided with an annular oil inlet chamber, an annular control oil chamber and a second oil return chamber which are interconnected; the second oil return chamber axially passes through the center of the circular valve block, and the annular oil inlet chamber is also connected to the liquid inlet passage; A plunger is respectively arranged in the annular oil inlet chamber and the annular control oil chamber and has a central hole; A slider is located in the second oil return chamber and is tightly fitted with the plunger; the slider is connected to the piston, and a channel assembly is provided on the slider to connect the annular oil inlet chamber with the annular control oil chamber, or connect the annular control oil chamber with the second oil return chamber when the slider reciprocates relative to the plunger under the drive of the piston; A hydraulic control unit is arranged in the valve body and located on the side of the circular valve block away from the piston; the hydraulic control unit is used to connect the oil outlet chamber with the liquid inlet channel, or connect the oil outlet chamber with the oil return chamber to perform reversal of the piston.

2. The anti-leakage automatic reciprocating supercharger according to claim 1, wherein The piston comprises: A small piston is close to the oil inlet chamber and fits tightly against the inner wall of the valve body; The large piston is nested outside the small piston and is located on the axial side of the small piston away from the oil inlet chamber; the large piston is tightly fitted with the inner wall of the valve body.

3. The anti-leakage automatic reciprocating supercharger according to claim 2, wherein, It also includes: A pull rod sleeve is arranged in the valve body; the first end of the pull rod sleeve is located on the side of the large piston away from the small piston, and is surrounded by the large piston to form the oil outlet cavity; the second end of the pull rod sleeve is inserted into the large piston, and is slidably matched with the large piston; A connecting component has one end located in the large piston and the other end extending into the second oil return chamber after passing through the pull rod sleeve and assembled with the slider to drive the slider to reciprocate under the drive of the piston.

4. The anti-leakage automatic reciprocating supercharger according to claim 3, wherein, The difference between the radial cross-sectional area of the large piston and the radial cross-sectional area of the pull rod sleeve is greater than the radial cross-sectional area of the small piston.

5. The anti-leakage automatic reciprocating supercharger according to claim 3, characterized in that, The connection component comprises: A pull rod, axially penetrating the pull rod sleeve; A limiting portion is located in the large piston and sleeved on the end of the pull rod; the limiting portion at least partially overlaps with the second end of the pull rod sleeve; The hook is located in the second oil return chamber and connected to the end of the pull rod away from the limiting portion; the hook is provided with a receiving position, and the receiving position has an opening; the slider is arranged in the receiving position, and the plunger is tightly fitted with the slider through the opening.

6. The anti-leakage automatic reciprocating supercharger according to claim 1, wherein The channel assembly comprises: A first channel having a first opening and a second opening; the first opening and the second opening are both located on the outer circumferential surface of the slider and are used to communicate with the annular oil inlet chamber and the annular control oil chamber respectively; The second passage has a third opening and a fourth opening; the third opening is located on the outer circumferential surface of the slider and is used for communicating with the annular control oil chamber; the fourth opening is located on the axial end surface of the slider on the side away from the piston and is used for communicating with the second oil return chamber.

7. The anti-leakage automatic reciprocating supercharger according to claim 1, characterized in that The hydraulic control unit includes: A hydraulic control ejector rod connected to the round valve block; a second oil inlet chamber communicating with the oil inlet passage is arranged at the axial end of the hydraulic control ejector rod on the side away from the round valve block; A sphere coaxially arranged with the hydraulic control ejector rod and close to the second oil inlet chamber; A hydraulic control valve assembly sleeved on the hydraulic control ejector rod and the sphere; A second oil outlet chamber communicating with the oil outlet chamber is provided between the hydraulic control valve assembly and the hydraulic control ejector rod, a third oil return chamber communicating with the liquid return passage is provided between the hydraulic control valve assembly and the sphere, and a third oil inlet chamber communicating with the oil inlet passage is arranged on the axial side of the hydraulic control valve assembly away from the round valve block; the hydraulic control valve assembly can reciprocate axially and drive the sphere to block the opening of the second oil inlet chamber to communicate the second oil outlet chamber with the third oil return chamber, or drive the sphere to open the opening of the second oil inlet chamber to communicate the second oil inlet chamber with the second oil outlet chamber.

8. The anti-leakage automatic reciprocating supercharger according to claim 7, characterized in that, The hydraulic control valve assembly includes: A hydraulic control valve sleeve sleeved on the hydraulic control ejector rod and capable of reciprocating axially; a through hole is provided on the hydraulic control valve sleeve, the through hole communicates with the opening of the second oil inlet chamber, and the diameter of the through hole is smaller than the diameter of the sphere; the second oil outlet chamber is located between the inner wall of the hydraulic control valve sleeve and the hydraulic control ejector rod; A valve sleeve is arranged at one end of the hydraulic control valve sleeve away from the round valve block; the third oil return chamber is located in the valve sleeve, and the sphere is located in the third oil return chamber; A valve core is arranged in the valve sleeve and on the side of the sphere away from the hydraulic control ejector rod to drive the sphere to block the opening of the second oil inlet chamber.

9. The anti-leakage automatic reciprocating supercharger according to claim 8, wherein, A slot is provided on the valve sleeve, a fourth oil return chamber is arranged in the valve body, and the fourth oil return chamber communicates with the oil return chamber; the hydraulic control ejector rod and the hydraulic control valve sleeve are both located in the fourth oil return chamber; the slot communicates with the third oil return chamber and the fourth oil return chamber respectively.

10. The anti-leakage automatic reciprocating supercharger according to claim 8, characterized in that, The difference between the radial cross-sectional area of the hydraulic control valve sleeve and the radial cross-sectional area of the part of the hydraulic control ejector rod located in the hydraulic control valve sleeve is greater than the radial cross-sectional area of the valve sleeve.

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