CN111237275B - A high pressure slide valve type check valve - Google Patents

Abstract

The invention belongs to the technical field of one-way hydraulic valves. In particular to a high-pressure slide valve type one-way valve. The technical proposal is as follows: the high-pressure slide valve type one-way valve comprises a valve body (3), a valve core (4), a spring (6), a left valve cover (1) and a right valve cover (8); the left valve cover (1) and the right valve cover (8) are arranged at the left end and the right end corresponding to the valve body (3) through bolts (16), the valve body (3) is internally provided with a valve core (4) and a spring (6), one end of the spring (6) is contacted with the right valve cover (8), and the other end of the spring (6) is contacted with the right end of the valve core (4); the right cylindrical surface of the valve core (4) is provided with a first combined sealing ring (11), the middle part of the inner wall of the valve body (3) is provided with a second combined sealing ring (13) near the right part, and the left cylindrical surface of the valve core (4) is provided with a third combined sealing ring (14); a left sealing ring (2) and a right sealing ring (7) are correspondingly arranged on the left end face and the right end face of the valve body (3). The invention has the characteristics of no hydraulic and mechanical impact, good sealing performance, good stability and long service life.

Description

A high pressure slide type check valve

Technical Field

The present invention belongs to the technical field of one-way hydraulic valves, and in particular relates to a high-pressure slide valve type one-way valve.

Background technique

At present, it is common to use one-way valves in hydraulic systems. The valve core structure is mostly conical or spherical. The existing one-way valve core and valve seat are mostly in line contact, which is prone to valve core dislocation. In addition, due to frequent opening and closing and vibration, the contact is easy to wear and produce grooves, which affects the sealing performance, makes the one-way valve unstable, and reduces the service life. In addition, when the hydraulic system is in high-frequency vibration, the one-way valve is also in high-frequency vibration, which causes the valve core and the valve seat to impact, thereby increasing the vibration and noise of the hydraulic system and affecting the working performance of the hydraulic system. When opening the high-pressure one-way valve, a small unloading valve must be added, making the structure of the high-pressure one-way valve more complicated.

From the current research situation, it is found that many scholars use software such as fluent to simulate the fluid of the one-way valve, and have made certain improvements to the structure, effectively solving the shortcomings of high noise, easy to get stuck, and poor opening speed. However, most of its valve core structures are still spherical or conical. "A hydraulically controlled one-way valve (CN209725330)" discloses a hydraulically controlled one-way valve with improved structure, which improves the contact performance between the spherical surface and the through hole, but the sealing performance still needs to be improved; "Ultra-high pressure hydraulically controlled one-way valve (CN209469836U)" discloses a one-way valve working under ultra-high pressure, which is provided with a piston that can be driven by liquid and can assist the movement of the ball core; "A high-pressure one-way valve controlled by an electromagnet (CN209761891U)" discloses a one-way valve controlled by an electromagnet, which improves the automatic control level of the one-way valve, and has the characteristics of not being affected by the return oil back pressure, fast response speed and no need to control the oil circuit. However, in the above technology, the valve core is a spherical or conical structure, and the contact between the valve core and the valve seat is still a line contact, which is easy to cause wear of the contact surface under mechanical impact and hydraulic impact, resulting in poor sealing and reduced service life.

Summary of the invention

The present invention aims to overcome the above-mentioned defects and has the object of providing a high-pressure slide-type one-way valve which can achieve no hydraulic and mechanical impact, good sealing, good stability and long service life.

In order to achieve the above object, the technical solution adopted by the present invention is:

The high-pressure slide valve type one-way valve comprises a valve body, a valve core, a spring, a left valve cover and a right valve cover. The left valve cover and the right valve cover are installed at the corresponding left and right ends of the valve body by bolts, the valve body is equipped with a valve core and a spring, one end of the spring is in contact with the right valve cover, and the other end of the spring is in contact with the right end of the valve core; the right cylindrical surface of the valve core is equipped with a first combined sealing ring, the middle right part of the inner wall of the valve body is equipped with a second combined sealing ring, and the left cylindrical surface of the valve core is equipped with a third combined sealing ring; the left end face and the right end face of the valve body are equipped with a left sealing ring and a right sealing ring respectively.

The valve body is tubular, with a first oil port on the right side of the middle of the valve body, and a second oil port on the right side of the first oil port. The opening of the first oil port faces upward, and the opening of the second oil port faces downward. The center line of the first oil port and the center line of the second oil port are located in the same section, and the distance L1 between the center line of the first oil port and the center line of the second oil port is 23-40 mm. The inner wall of the valve body is provided with a first countersunk groove and a second countersunk groove, and the center line of the groove width of the first countersunk groove is located in the same section as the center line of the first oil port, and the center line of the groove width of the second countersunk groove is located in the same section as the center line of the second oil port; the inner wall of the valve body is provided with a second sealing groove, and the second sealing groove is located in the middle of the first countersunk groove and the second countersunk groove, and the second sealing groove is equipped with a second combined sealing ring; the two side surfaces of the second countersunk groove are symmetrical annular inclined surfaces, and the angle between the annular inclined surfaces and the inner wall is 40-45°.

A control oil channel is provided in the valve body shell along the axis, the oil outlet of the control oil channel is communicated with the left cavity of the valve body, the oil inlet of the control oil channel is communicated with the second oil port, and the distance L2 between the oil outlet of the control oil channel and the left end face of the valve body is 20-25 mm; the left end face and the right end face of the valve body are correspondingly provided with a left sealing groove and a right sealing groove, and the left sealing groove and the right sealing groove are correspondingly provided with a left sealing ring and a right sealing ring.

The valve core is a whole composed of a core rod, a left cylinder at the left end of the core rod, and a right cylinder at the right end of the core rod. A third sealing groove is provided in the middle of the left cylinder, and a third combined sealing ring is installed in the third sealing groove; a first sealing groove is provided 5 to 10 mm away from the right end face of the right cylinder, and a first combined sealing ring is installed in the first sealing groove; the third sealing groove is the same as the first sealing groove, and the first combined sealing ring is the same as the third combined sealing ring. A right circular boss is coaxially provided on the right end face of the right cylinder, and the right circular boss is the core shaft of the spring. The diameter of the right circular boss is the same as the inner diameter of the spring. A conical surface is formed between the left end face of the right cylinder and the cylindrical surface.

The clearance between the diameter of the left cylinder and the right cylinder of the valve core and the inner wall of the valve body is 5 to 10 μm.

A left circular boss is coaxially arranged inside the left valve cover, and a height L3 of the left circular boss is equal to a distance L2 between the oil outlet of the control oil passage and the left end face of the valve body. Screw holes are evenly arranged on the left valve cover.

A blind hole is arranged at the center of the right valve cover, the blind hole is a spring seat, an oil leakage port is arranged at the center of the blind hole, and screw holes are evenly arranged on the right valve cover.

The free length of the spring is 45 to 80 mm, and the compression amount is 22 to 40 mm.

In the closed state, the distance between the intersection line of the conical surface and the cylindrical surface of the right cylinder and the left side surface of the second sealing ring is 0.5-1 mm.

The third combined sealing ring is composed of an inner sealing ring for the valve core and an outer sealing ring for the valve core. The cross section of the outer sealing ring for the valve core is rectangular; the cross section of the inner sealing ring for the valve core is in the shape of an "I" character, the two sides of the cross section of the inner sealing ring for the valve core are symmetrical arcs, and the middle width of the inner sealing ring for the valve core is 3 to 4 mm; the width of the inner sealing ring for the valve core and the width of the outer sealing ring for the valve core are the same as the nominal size of the width of the third sealing groove, which is 5 to 6 mm; the height of the inner sealing ring for the valve core is 3 to 5 mm, the height of the outer sealing ring for the valve core is 2 to 3 mm, and the sum of the height of the inner sealing ring for the valve core and the height of the outer sealing ring for the valve core is the same as the nominal size of the height of the third sealing groove.

The second combined sealing ring is composed of an inner sealing ring for the valve body and an outer sealing ring for the valve body. The cross-sectional shape of the inner sealing ring for the valve body is the same as that of the outer sealing ring for the valve core, and the cross-sectional shape of the outer sealing ring for the valve body is the same as that of the inner sealing ring for the valve core.

The valve body and the valve core are both made of 45# steel.

The cone angle of the conical surface is 30-35°, and the generatrix length is 3-5 mm.

The diameter of the left circular boss is 0.35 to 0.5 times the diameter of the valve core.

The material of the inner sealing ring for the valve core is oil-resistant rubber material.

The material of the outer sealing ring for the valve core is tetrafluoroethylene material.

The material of the inner sealing ring for the valve body is tetrafluoroethylene material.

The material of the outer sealing ring for the valve body is oil-resistant rubber material.

Due to the adoption of the above technical solution, the present invention has the following advantages compared with the prior art:

1. When high-pressure oil enters from the second oil port and enters the left chamber through the control oil channel, the high-pressure oil acts on the left end face of the valve core, pushing the valve core to move to the right, the spring is compressed, the valve port is opened (the second oil port is connected to the first oil port), and the high-pressure oil flows from the second oil port to the first oil port. Since the valve core is a sliding valve structure and is not prone to misalignment, the force acting on the left end face of the valve core makes the valve core move quickly and smoothly.

2. When the second oil port is in low-pressure oil return, the spring pushes the valve core to move left and reset, and can also limit the position; close the valve port, cut off the second oil port and the first oil port, prevent the oil in the upper part of the first oil port from flowing out, and the valve core moves accurately, ensuring the stability of the high-pressure slide valve type check valve, while avoiding the hydraulic oil inside the related actuators from flowing out.

3. The left end face of the right cylinder of the valve core of the present invention is processed with a conical surface, the cone angle of the conical surface is 30-35°, and the generatrix length is 3-5mm, so as to mitigate the impact of high-pressure oil. In the closed state, the distance between the intersection of the conical surface and the cylindrical surface of the right cylinder and the left side of the second sealing ring is 0.5-1mm, and the matching clearance between the valve body and the valve core is 5-10μm, which plays a role in gap sealing, reduces the leakage of hydraulic oil caused by the matching clearance, and makes the high-pressure slide valve type check valve have good sealing performance.

4. A third sealing groove is provided in the middle of the left cylinder of the valve core, and a third combined sealing ring is installed in the third sealing groove; a first sealing groove is provided 5 to 10 mm away from the right end face of the right cylinder, and a first combined sealing ring is installed in the first sealing groove. This effectively reduces the leakage of hydraulic oil, making the sealing performance of the high-pressure slide valve type check valve good.

The first combined sealing ring and the third combined sealing ring are both composed of an inner sealing ring 31 for the valve core and an outer sealing ring 32 for the valve core. The cross-section of the outer sealing ring 32 for the valve core is a rectangular surface with a width of 5 to 6 mm and a height of 2 to 3 mm, and is made of tetrafluoroethylene material; the cross-section of the inner sealing ring 31 for the valve core is in the shape of an "I" character with a width of 5 to 6 mm and a height of 3 to 5 mm, with symmetrical arcs on both sides and a width of 3 to 4 mm in the middle, and is made of oil-resistant rubber material.

The second combined seal ring is composed of an inner seal ring for the valve body and an outer seal ring for the valve body. The cross-sectional shape of the inner seal ring for the valve body is the same as that of the outer seal ring for the valve core, and the material is tetrafluoroethylene; the cross-sectional shape of the outer seal ring for the valve body is the same as that of the inner seal ring for the valve core, and the material is oil-resistant rubber material. The leakage of hydraulic oil is significantly reduced, and the sealing performance is effectively improved. The seal of the combined seal ring and the annular gap seal play a double-channel sealing role for the high-pressure slide valve type check valve, and the sealing performance is good.

5. A blind hole is provided in the center of the right valve cover. The blind hole is a spring seat. An oil leakage port is provided in the center of the blind hole. When the valve core moves to the right, the leaked oil inside the right cavity is discharged through the oil leakage port, avoiding the leakage oil from forming back pressure in the right cavity, making the movement of the valve core fast and smooth.

6. During the left movement of the valve core, the hydraulic oil in the left chamber flows back to the oil tank through the control oil channel. The hydraulic oil in the left chamber plays a buffering role, avoiding the mechanical impact between the left end face of the left cylinder of the valve core and the left circular boss of the left valve cover, making the valve core move smoothly and avoiding hydraulic shock, thereby extending the service life of the high-pressure slide valve type check valve.

Therefore, the present invention has the characteristics of no hydraulic and mechanical impact, good sealing, good stability and long service life.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG1 is a schematic structural diagram of the present invention;

FIG2 is a schematic structural diagram of the valve body 3 in FIG1 ;

FIG3 is a schematic structural diagram of the valve core 4 in FIG1 ;

FIG4 is a schematic structural diagram of the left valve cover 1 in FIG1 ;

FIG5 is a schematic structural diagram of the right valve cover 8 in FIG1 ;

FIG6 is a schematic structural diagram of the third combined sealing ring 14 in FIG1 ;

FIG. 7 is a schematic structural diagram of the second combined sealing ring 13 in FIG. 1 .

Detailed ways

The present invention is further described below in conjunction with the accompanying drawings and specific embodiments, which does not limit the protection scope of the present invention.

In this specific implementation mode:

The valve body 3 and the valve core 4 are both made of 45# steel.

The cone angle of the conical surface 26 is 30-35°, and the generatrix length is 3-5 mm.

The diameter of the left circular boss is 0.35 to 0.5 times the diameter of the valve core 4 .

The material of the inner sealing ring 31 for the valve core is oil-resistant rubber material.

The material of the valve core outer sealing ring 32 is tetrafluoroethylene.

The valve body inner sealing ring 33 is made of tetrafluoroethylene.

The material of the valve body outer sealing ring 34 is oil-resistant rubber material.

This will not be described in detail in the embodiments.

Example 1

A high-pressure slide valve type one-way valve. As shown in FIG1 , the high-pressure slide valve type one-way valve comprises a valve body 3, a valve core 4, a spring 6, a left valve cover 1 and a right valve cover 8. The left valve cover 1 and the right valve cover 8 are installed at the corresponding left and right ends of the valve body 3 by bolts 16, and the valve core 4 and the spring 6 are installed in the valve body 3, one end of the spring 6 is in contact with the right valve cover 8, and the other end of the spring 6 is in contact with the right end of the valve core 4; the right cylindrical surface of the valve core 4 is equipped with a first combined sealing ring 11, the middle right part of the inner wall of the valve body 3 is equipped with a second combined sealing ring 13, and the left cylindrical surface of the valve core 4 is equipped with a third combined sealing ring 14; the left end face and the right end face of the valve body 3 are equipped with a left sealing ring 2 and a right sealing ring 7 respectively.

As shown in FIG. 2 , the valve body 3 is tubular, with a first oil port 5 on the right side of the middle of the valve body 3, and a second oil port 12 on the right side of the first oil port 5. The opening of the first oil port 5 faces upward, and the opening of the second oil port 12 faces downward. The center line of the first oil port 5 and the center line of the second oil port 12 are located in the same cross section, and the distance L1 between the extension line of the center line of the first oil port 5 and the extension line of the center line of the second oil port 12 is 23 to 30 mm. A first undercut groove 20 and a second undercut groove 18 are formed on the inner wall of the valve body 3, wherein the centerline of the groove width of the first undercut groove 20 and the centerline of the first oil port 5 are located in the same cross section, and the centerline of the groove width of the second undercut groove 18 and the centerline of the second oil port 12 are located in the same cross section; a second sealing groove 19 is formed on the inner wall of the valve body 3, wherein the second sealing groove 19 is located in the middle position between the first undercut groove 20 and the second undercut groove 18, and the second sealing groove 19 is equipped with a second combined sealing ring 13; the two side surfaces of the second undercut groove 18 are symmetrical annular inclined surfaces, and the angle between the annular inclined surfaces and the inner wall is 40 to 43°.

As shown in Figure 2, a control oil channel 15 is provided in the shell of the valve body 3 along the axis, the oil outlet of the control oil channel 15 is communicated with the left chamber 17 of the valve body 3, the oil inlet of the control oil channel 15 is communicated with the second oil port 12, and the distance L2 between the oil outlet of the control oil channel 15 and the left end face of the valve body 3 is 20-23 mm; the left end face and the right end face of the valve body 3 are correspondingly provided with a left sealing groove 21 and a right sealing groove 22, and the left sealing groove 21 and the right sealing groove 22 are correspondingly provided with a left sealing ring 2 and a right sealing ring 7.

As shown in FIG3 , the valve core 4 is an integral body consisting of a core rod 27, a left cylinder 28 at the left end of the core rod 27, and a right cylinder 25 at the right end of the core rod 27. A third sealing groove 29 is provided in the middle of the left cylinder 28, and a third combined sealing ring 14 is installed in the third sealing groove 29; a first sealing groove 24 is provided at a distance of 5 to 10 mm from the right end face of the right cylinder 25, and a first combined sealing ring 11 is installed in the first sealing groove 24; the third sealing groove 29 is the same as the first sealing groove 24, and the first combined sealing ring 11 is the same as the third combined sealing ring 14. A right circular boss 23 is coaxially provided on the right end face of the right cylinder 25, and the right circular boss 23 is the core shaft of the spring 6, and the diameter of the right circular boss 23 is the same as the inner diameter of the spring 6, and a conical surface 26 is provided between the left end face and the cylindrical surface of the right cylinder 25.

As shown in FIG. 1 , the clearance between the diameter of the left cylinder 28 and the right cylinder 25 of the valve core 4 and the inner wall of the valve body 3 is 5 to 8 μm.

As shown in Figures 1, 2 and 4, a left circular boss is coaxially provided on the inner side of the left valve cover 1, and the height L3 of the left circular boss is equal to the distance L2 between the oil outlet of the control oil channel 15 and the left end surface of the valve body 3. Screw holes are evenly provided on the left valve cover 1.

As shown in FIG. 1 and FIG. 5 , a blind hole 30 is provided at the center of the right valve cover 8 , and the blind hole 30 is a spring seat. An oil leakage port 9 is provided at the center of the blind hole 30 , and screw holes are also evenly provided on the right valve cover 8 .

As shown in FIG. 1 , the free length of the spring 6 is 45 to 70 mm, and the compression amount is 22 to 35 mm.

As shown in FIG. 1 , in the closed state of the present embodiment 1, the distance between the intersection line of the conical surface 26 and the cylindrical surface of the right cylinder 25 and the left side surface of the second sealing ring 13 is 0.5-1 mm.

As shown in FIG6 , the third combined seal ring 14 is composed of an inner seal ring 31 for the valve core and an outer seal ring 32 for the valve core. The cross section of the outer seal ring 32 for the valve core is rectangular; the cross section of the inner seal ring 31 for the valve core is in the shape of an “I” character, the two sides of the cross section of the inner seal ring 31 for the valve core are symmetrical arcs, and the width of the middle part of the inner seal ring 31 for the valve core is 3 to 4 mm; the width of the inner seal ring 31 for the valve core and the width of the outer seal ring 32 for the valve core are the same as the nominal size of the width of the third sealing groove 29, which is 5 to 6 mm; the height of the inner seal ring 31 for the valve core is 3 to 5 mm, the height of the outer seal ring 32 for the valve core is 2 to 3 mm, and the sum of the height of the inner seal ring 31 for the valve core and the height of the outer seal ring 32 for the valve core is the same as the nominal size of the height of the third sealing groove 29.

As shown in Fig. 7, the second combined seal ring 13 is composed of an inner seal ring 33 for the valve body and an outer seal ring 34 for the valve body. The cross-sectional shape of the inner seal ring 33 for the valve body is the same as the cross-sectional shape of the outer seal ring 32 for the valve core, and the cross-sectional shape of the outer seal ring 34 for the valve body is the same as the cross-sectional shape of the inner seal ring 31 for the valve core.

Example 2

A high-pressure slide-type one-way valve. Except for the following technical parameters, the rest is the same as Example 1:

The distance L1 between the extension line of the center line of the first oil port 5 and the extension line of the center line of the second oil port 12 is 30-40 mm.

The angle between the annular slope and the inner wall is 42-45°

The distance L2 between the oil outlet of the control oil passage 15 and the left end surface of the valve body 3 is 22-25 mm;

The clearance between the diameter of the left cylinder 28 and the right cylinder 25 of the valve core 4 and the inner wall of the valve body 3 is 7-10 μm.

The free length of the spring 6 is 55 to 80 mm, and the compression amount is 30 to 40 mm.

Compared with the prior art, this specific implementation has the following advantages:

1. When high-pressure oil enters from the second oil port 12 and enters the left chamber 17 through the control oil channel 15, the high-pressure oil acts on the left end face of the valve core 4, pushing the valve core 4 to move to the right, the spring 6 is compressed, the valve port is opened (the second oil port 12 is connected to the first oil port 5), and the high-pressure oil flows from the second oil port 12 to the first oil port 5. Since the valve core 4 is a sliding valve structure and is not easily misplaced, the force acting on the left end face of the valve core 4 makes the valve core 4 move quickly and smoothly.

2. When the second oil port 12 is in low-pressure oil return, the spring 6 pushes the valve core 4 to move left and reset, and can also limit the position; close the valve port, cut off the second oil port 12 and the first oil port 5, prevent the oil in the upper part of the first oil port 5 from flowing out, and the valve core 4 moves to an accurate position, ensuring the stability of the high-pressure slide valve type check valve, while avoiding the hydraulic oil inside the relevant actuator from flowing out.

3. The left end face of the right cylinder 25 of the valve core 4 of this specific embodiment is processed with a conical surface 26, the cone angle of the conical surface 26 is 30-35°, and the generatrix length is 3-5mm, so as to mitigate the impact of high-pressure oil. In the closed state, the distance between the intersection of the conical surface 26 and the cylindrical surface of the right cylinder 25 and the left side of the second sealing ring 13 is 0.5-1mm, and the matching clearance between the valve body 3 and the valve core 4 is 5-10μm, which plays a role in gap sealing, reduces the leakage of hydraulic oil caused by the matching clearance, and makes the sealing performance of the high-pressure slide valve type check valve good.

4. A third sealing groove 29 is provided in the middle of the left cylinder 28 of the valve core 4, and a third combined sealing ring 14 is installed in the third sealing groove 29; a first sealing groove 24 is provided at a distance of 5 to 10 mm from the right end surface of the right cylinder 25, and a first combined sealing ring 11 is installed in the first sealing groove 24. The leakage of hydraulic oil is effectively reduced, so that the sealing performance of the high-pressure slide valve type check valve is good.

The first combined sealing ring 11 and the third combined sealing ring 14 are both composed of an inner sealing ring 31 for the valve core and an outer sealing ring 32 for the valve core. The cross-section of the outer sealing ring 32 for the valve core is a rectangular surface with a width of 5 to 6 mm and a height of 2 to 3 mm, and is made of tetrafluoroethylene material; the cross-section of the inner sealing ring 31 for the valve core is in the shape of an "I" character with a width of 5 to 6 mm and a height of 3 to 5 mm, with symmetrical arcs on both sides and a width of 3 to 4 mm in the middle, and is made of oil-resistant rubber material.

The second combined seal ring 13 is composed of an inner seal ring 33 for the valve body and an outer seal ring 34 for the valve body. The cross-sectional shape of the inner seal ring 33 for the valve body is the same as that of the outer seal ring 32 for the valve core, and the material is tetrafluoroethylene; the cross-sectional shape of the outer seal ring 34 for the valve body is the same as that of the inner seal ring 31 for the valve core, and the material is oil-resistant rubber material. The leakage of hydraulic oil is significantly reduced, and the sealing performance is effectively improved. The sealing of the combined seal ring and the annular gap seal play a double-channel sealing role for the high-pressure slide valve type check valve, and the sealing performance is good.

5. A blind hole 30 is provided at the center of the right valve cover 8. The blind hole 30 is a spring seat. An oil leakage port 9 is provided at the center of the blind hole 30. When the valve core 4 moves to the right, the leaked oil inside the right cavity 10 is discharged through the oil leakage port 9, thereby avoiding the leakage oil from forming back pressure in the right cavity 10, so that the movement process of the valve core 4 is fast and smooth.

6. During the left movement of the valve core 4, the hydraulic oil in the left chamber 17 flows back to the oil tank through the control oil channel 15. The hydraulic oil in the left chamber 17 plays a buffering role, avoiding the mechanical impact between the left end face of the left cylinder 28 of the valve core 4 and the left circular boss of the left valve cover 1, so that the valve core 4 moves smoothly, avoiding hydraulic shock, and thus extending the service life of the high-pressure slide valve type check valve.

Therefore, the present specific implementation has the characteristics of no hydraulic and mechanical impact, good sealing, good stability and long service life.

Claims (7)

1. A high-pressure sliding valve type one-way valve, characterized in that the high-pressure sliding valve type one-way valve comprises a valve body (3), a valve core (4), a spring (6), a left valve cover (1) and a right valve cover (8); the left valve cover (1) and the right valve cover (8) are installed at the corresponding left and right ends of the valve body (3) by bolts (16); the valve core (4) and the spring (6) are installed in the valve body (3); one end of the spring (6) is in contact with the right valve cover (8), and the other end of the spring (6) is in contact with the right end of the valve core (4); the right cylindrical surface of the valve core (4) is equipped with a first combined sealing ring (11), the middle right part of the inner wall of the valve body (3) is equipped with a second combined sealing ring (13), and the left cylindrical surface of the valve core (4) is equipped with a third combined sealing ring (14); the left end surface and the right end surface of the valve body (3) are equipped with a left sealing ring (2) and a right sealing ring (7) respectively; The valve body (3) is tubular, with a first oil port (5) opened at the right side of the middle of the valve body (3), and a second oil port (12) opened on the right side of the first oil port (5), the opening of the first oil port (5) faces upward, and the opening of the second oil port (12) faces downward, the center line of the first oil port (5) and the center line of the second oil port (12) are located in the same cross section, and the distance L1 between the center line of the first oil port (5) and the center line of the second oil port (12) is 23-40 mm; a first undercut groove (20) and a second undercut groove (18) are opened on the inner wall of the valve body (3), and the first undercut groove The center line of the groove width of the second recessed groove (20) and the center line of the first oil port (5) are located in the same cross section, and the center line of the groove width of the second recessed groove (18) and the center line of the second oil port (12) are located in the same cross section; a second sealing groove (19) is opened on the inner wall of the valve body (3), the second sealing groove (19) is located at the middle position between the first recessed groove (20) and the second recessed groove (18), and the second sealing groove (19) is equipped with a second combined sealing ring (13); the two side surfaces of the second recessed groove (18) are symmetrical annular inclined surfaces, and the angle between the annular inclined surfaces and the inner wall is 40-45 degrees; A control oil passage (15) is provided on the housing of the valve body (3) along the axis, the oil outlet of the control oil passage (15) is communicated with the left chamber (17) of the valve body (3), the oil inlet of the control oil passage (15) is communicated with the second oil port (12), and the distance L2 between the oil outlet of the control oil passage (15) and the left end face of the valve body (3) is 20-25 mm; the left end face and the right end face of the valve body (3) are respectively provided with a left sealing groove (21) and a right sealing groove (22), and the left sealing groove (21) and the right sealing groove (22) are respectively provided with a left sealing ring (2) and a right sealing ring (7); The valve core (4) is an integral body consisting of a core rod (27), a left cylinder (28) at the left end of the core rod (27), and a right cylinder (25) at the right end. A third sealing groove (29) is provided in the middle of the left cylinder (28), and a third combined sealing ring (14) is installed in the third sealing groove (29). A first sealing groove (24) is provided at a distance of 5 to 10 mm from the right end surface of the right cylinder (25), and a first combined sealing ring (14) is installed in the first sealing groove (24). 1); the third sealing groove (29) is the same as the first sealing groove (24); the first combined sealing ring (11) is the same as the third combined sealing ring (14); the right end face of the right cylinder (25) is coaxially provided with a right circular boss (23); the right circular boss (23) is the core shaft of the spring (6); the diameter of the right circular boss (23) is the same as the inner diameter of the spring (6); the left end face of the right cylinder (25) and the cylindrical surface are between a conical surface (26); The clearance between the diameter of the left cylinder (28) and the right cylinder (25) of the valve core (4) and the inner wall of the valve body (3) is 5-10 μm; A left circular boss is coaxially disposed on the inner side of the left valve cover (1), and a height L3 of the left circular boss is equal to a distance L2 between the oil outlet of the control oil passage (15) and the left end surface of the valve body (3); A blind hole (30) is provided at the center of the right valve cover (8), the blind hole (30) is a spring seat, and an oil leakage port (9) is provided at the center of the blind hole (30); The free length of the spring (6) is 45-80 mm, and the compression amount is 22-40 mm; In the closed state, the distance between the intersection of the conical surface (26) and the cylindrical surface of the right cylinder (25) and the left side surface of the second combined sealing ring (13) is 0.5-1 mm; The third combined sealing ring (14) is composed of an inner sealing ring (31) for the valve core and an outer sealing ring (32) for the valve core; the cross section of the outer sealing ring (32) for the valve core is rectangular, the cross section of the inner sealing ring (31) for the valve core is in the shape of an I, the two sides of the cross section of the inner sealing ring (31) for the valve core are symmetrical arcs, and the width of the middle part of the inner sealing ring (31) for the valve core is 3-4 mm; the width of the inner sealing ring (31) for the valve core and the width of the outer sealing ring (32) for the valve core are the same as the nominal size of the width of the third sealing groove (29), and the width is 5-6 mm; the height of the inner sealing ring (31) for the valve core is 3-5 mm, the height of the outer sealing ring (32) for the valve core is 2-3 mm, and the sum of the height of the inner sealing ring (31) for the valve core and the height of the outer sealing ring (32) for the valve core is the same as the nominal size of the height of the third sealing groove (29); The second combined sealing ring (13) is composed of an inner sealing ring (33) for the valve body and an outer sealing ring (34) for the valve body; the cross-sectional shape of the inner sealing ring (33) for the valve body is the same as the cross-sectional shape of the outer sealing ring (32) for the valve core, and the cross-sectional shape of the outer sealing ring (34) for the valve body is the same as the cross-sectional shape of the inner sealing ring (31) for the valve core; The material of the valve body outer sealing ring (34) is oil-resistant rubber material. 2. The high-pressure sliding valve type one-way valve according to claim 1 is characterized in that the valve body (3) and the valve core (4) are both made of 45 steel. 3. The high-pressure sliding valve type one-way valve according to claim 1 is characterized in that the cone angle of the conical surface (26) is 30~35° and the generatrix length is 3~5mm. 4. The high-pressure sliding valve type one-way valve according to claim 1 is characterized in that the diameter of the left circular boss is 0.35 to 0.5 times the diameter of the valve core (4). 5. The high-pressure sliding valve type one-way valve according to claim 1 is characterized in that the material of the inner sealing ring (31) for the valve core is oil-resistant rubber material. 6. The high-pressure sliding valve type one-way valve according to claim 1, characterized in that the material of the outer sealing ring (32) for the valve core is tetrafluoroethylene material. 7. The high-pressure sliding valve type one-way valve according to claim 1, characterized in that the inner sealing ring (33) for the valve body is made of tetrafluoroethylene material.