Long-life sliding vane and multi-purpose sliding vane pump

Abstract

The present application relates to the field of pump, specifically to a long service life sliding vane, both sides of the sliding vane are cambered surface sections, and there is a gap between the cambered surface sections and the sliding vane groove, so that the sliding vane can rotate in the sliding vane groove through the cambered surface sections, the mating surface of the sliding vane and the inner wall of the pump body has at least two linear seals, the two linear seals of the sliding vane and the inner wall of the pump body, the two linear seals of the sliding vane and the inner wall of the pump body form a sealed cavity. The present application greatly improves the service life of the sliding vane; the present application also provides a multi-purpose sliding vane pump. The present application can meet the use under different complex working conditions at the same time through a sliding vane pump.

Description

Technical Field

[0001] This invention relates to the field of pumps, specifically a long-life vane pump and a multi-purpose vane pump. Background Technology

[0002] A vane pump, also known as a centrifugal pump, scraper pump, or scraper vane pump, is a rotary positive displacement pump. Due to its simple structure, good self-priming performance, high efficiency, and convenient maintenance, it is widely used in oil depots for tank transfer, unloading and cleaning of tanks on trains and trucks, loading and unloading and cleaning of tanks on oil tankers, lubricating oil transportation, and bottom oil extraction in vacuum systems. The rotor of a vane pump is a cylinder with radial grooves, in which vanes are placed and can slide freely. The rotor is eccentrically mounted inside the pump body. When the rotor rotates, the vanes are pressed tightly against the inner wall of the pump body by centrifugal force or spring force. In the first half of the rotor's rotation, the space enclosed by adjacent vanes gradually increases, creating a partial vacuum and drawing in liquid. In the second half of the rotation, this space gradually decreases, compressing the liquid and forcing it out. This process repeats, thus achieving the pumping action.

[0003] In traditional vane pumps, to ensure a reliable seal between the impeller rotor and the pump body wall during operation, the vanes must be tightly fitted against the pump body wall at all positions. Therefore, high-pressure fluid is typically introduced into the root space of the vanes to achieve a self-tightening seal. However, under radial pressure, the root pressure of the vanes increases, generating localized high temperatures at the contact point between the vanes and the pump body. This can cause localized annealing, leading to rapid wear of the vanes. Simultaneously, due to the pressure difference between the pump body's suction and discharge zones, the vanes experience uneven force on both sides as they move from the low-pressure zone to the high-pressure zone. The larger lateral force on the vanes results in significant friction between the vanes and the inner groove surface of the impeller rotor, causing rapid wear and a short service life.

[0004] Furthermore, existing vane pumps, whether single-acting or double-acting, all have a single rotating pump rotor (rotating disc) with a pair of suction and discharge ports. This limits the pump's ability to transport media in a single line, making it unable to meet more complex operating conditions. Therefore, this issue urgently needs to be addressed. Summary of the Invention

[0005] To avoid and overcome the technical problems existing in the prior art, this invention provides a long-life vane, which significantly improves the service life of the vane; this invention also provides a multi-purpose vane pump. This invention, through a single vane pump, can simultaneously meet the needs of various complex working conditions.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] A long-life sliding vane has arc-shaped sections on both sides, and there is a gap between the arc-shaped sections and the sliding vane groove, so that the sliding vane can rotate in the sliding vane groove through the arc-shaped sections. There are at least two line seals between the sliding vane and the inner wall of the pump body, so that the sliding vane and the inner wall of the pump body can be enclosed to form a sealed cavity.

[0008] As a further aspect of the present invention: the mating surface between the sliding vane and the inner wall of the pump body is a plane, and the two sides of the plane contact the inner wall of the pump body to form a two-segment line seal; a through hole is provided on the sliding vane, and the medium enters the sealing cavity after passing through the gap between the arc section and the sliding vane groove and the through hole in sequence.

[0009] As a further embodiment of the present invention: a spring groove for positioning the spring is provided at the bottom of the slide plate, and a pressure reducing groove is provided on the mating surface between the slide plate and the inner wall of the pump body. The connecting hole passes through the spring groove and the pressure reducing groove in sequence along the axial direction of the slide plate.

[0010] As a further aspect of the present invention: the radius SR of the arc segment is:

[0011]

[0012] Let b be the midpoint of any arc segment, and c be the intersection of the axis of the sliding vane and the inner wall of the pump body.

[0013] Where L2 is the distance from point b to point c;

[0014] L1 is the distance from the center of gravity of the slider to point c;

[0015] R is the maximum radius of the inner circular curve of the stator;

[0016] r is the minimum radius of the inner circular curve of the stator;

[0017] δ is the thickness of the slider;

[0018] z represents the number of vanes in the vane pump;

[0019] Q is the design flow rate of the vane pump;

[0020] n is the rotational speed of the vane pump;

[0021] B is the axial length of the slider.

[0022] A multi-purpose vane pump comprises at least two sets of independently transportable media working sections arranged axially along the pump shaft. The vanes are installed in vane slots on the rotors of each working section. Each working section is equipped with an inlet and an outlet, and the rotors of each working section are coaxially fixed to the pump shaft. The media enters the suction chamber through the inlet and is transported by the rotor, then discharged outwards through the outlet of the discharge chamber. The working sections cooperate to achieve the following three operating modes:

[0023] Each working section is connected to a different media source and operates independently of the others;

[0024] The suction inlets of each working section are connected to the same medium source through parallel inlet pipes, and the discharge outlets of each working section are connected through parallel outlet pipes to discharge the medium in parallel.

[0025] The suction port of the working section at the first end is connected to the medium source. Along the pump shaft axis, the discharge port of each working section is connected to the suction port of the next working section through a booster pipe to continuously pressurize the medium, which is then discharged outward through the discharge port of the working end at the tail end.

[0026] As a further embodiment of the present invention: along the pump shaft axis, one end of the working section is open to facilitate the assembly of the rotor, and adjacent working sections are connected by a connecting section to close the opening of the working section.

[0027] As a further aspect of the present invention: a sealing cavity is provided in the connecting section, and two sets of skeleton oil seals arranged coaxially with the pump shaft are provided in the sealing cavity. The two skeleton oil seals abut and are arranged symmetrically to prevent the medium from flowing across adjacent working sections. A drainage hole is provided on the connecting section to communicate with the contact surface of the two skeleton oil seals to drain the leaked medium.

[0028] As a further aspect of the present invention: sealing rings are installed at the contact surfaces of the connecting section and the two adjacent working sections to prevent leakage; the opening of the working section at the tail end is closed by the pump cover, and the pump cover, each working section and each connecting section are coaxially fixed by bolts.

[0029] As a further embodiment of the present invention: the pump shaft is equipped with a shaft end seal to prevent leakage. The shaft end seal is a skeleton oil seal, and the sealing cavity where the shaft end seal is located is connected to the discharge cavity of the adjacent working section through a pressure relief hole.

[0030] As a further embodiment of the present invention: each working section is coaxially rotated with the pump shaft via sliding bearings; flow meters, temperature sensors and pressure sensors are installed on the booster pipe, parallel inlet pipe and parallel outlet pipe.

[0031] Compared with the prior art, the beneficial effects of the present invention are:

[0032] 1. This invention designs the sliding vane with at least two segments of line seals against the inner wall of the pump body. This increases the reliability of the seal and gives the vane a wear self-compensation function. That is, when one segment of the line seal is worn excessively, it can still ensure that the other segment of the line seal can fit against the inner wall of the pump body, indirectly extending the service life of the vane. At the same time, the arc design on both sides of the vane allows the vane to rotate within the vane groove. The tilt angle of the vane is adjustable throughout the entire movement cycle. This solves the problems of traditional vanes being prone to wedging under large extension and easy side wear in the high-low pressure transition zone. It also improves the poor matching between the traditional vane and the impact load it receives under large tilt angle conditions, enabling the vane to operate stably for a long time.

[0033] 2. By opening a connecting hole on the vane, the high-pressure medium can pass through the gap between the arc section and the vane groove, as well as the connecting hole, into the sealing cavity to balance the pressure, reduce the line contact pressure between the vane and the pump body wall, reduce the friction between the vane and the pump body wall, and further improve the service life of the vane. The setting of the pressure reducing groove further increases the surface area of ​​the medium in contact with the medium in the sealing cavity, and further reduces the pressure. By establishing the arc radius formula, the optimal arc section radius can be calculated under different design flow rates of the vane pump, so that the wear of the line seal can be kept at a minimum after the vane rotates.

[0034] 3. This invention can simultaneously transport various media by arranging multiple working sections coaxially on the pump shaft, or by arranging the working sections in parallel to transport a large flow of media, or by arranging the working sections in series to pressurize and transport media. Only the pump shaft is needed as a power source to enable the vane pump to meet the needs of different complex working conditions.

[0035] 4. The open arrangement of the working section of the present invention facilitates the installation of the rotor. After the rotor is installed, adjacent working sections can be connected and sealed through the connecting section. The arrangement of the double skeleton oil seal in the connecting section can ensure that the rotors of adjacent working sections work independently and avoid cross-flow of the medium. The medium with slight leakage between the two working sections can be directly led out through the drainage hole.

[0036] 5. The alternating detachable arrangement of the working section and connecting section of this invention, connected in series, allows for the increase or decrease of the number of working sections to suit different operating conditions, and is easy to assemble and disassemble. The working section and the pump shaft are connected by a sliding bearing, which provides shaft support and effectively avoids wear between the shaft and the working section, extending the service life of the pump shaft and effectively reducing the radial dimension of the pump, making the overall structure of the pump simpler and more compact.

[0037] 6. The pressure relief hole of the present invention connects the sealing cavity and the discharge cavity of the working section. Since the discharge cavity is a high-pressure cavity, the high-pressure medium can be led to the shaft end seal through the pressure relief hole, and then flow back to the pump cavity of the working section through the gap between the pump shaft and the sliding bearing, preventing outside air from entering the working section while lubricating the sliding bearing. Attached Figure Description

[0038] Figure 1 This is a schematic diagram of the structure of the present invention.

[0039] Figure 2 This is a schematic diagram of the structure under the first working condition in this invention.

[0040] Figure 3 This is a schematic diagram of the structure under the second working condition in this invention.

[0041] Figure 4 This is a schematic diagram of the structure under the third working condition in this invention.

[0042] Figure 5 This is a schematic diagram of the slider in this invention.

[0043] Figure 6 This is a schematic diagram of the inner circular curve of the stator in this invention.

[0044] Figure 7 This is a schematic diagram of the motion state of the slider in this invention.

[0045] Figure 8 This is a static strength analysis diagram of a traditional slider.

[0046] Figure 9 This is a static strength analysis diagram of the slider of the present invention.

[0047] In the picture:

[0048] 1. Working section; 11. Inlet; 12. Inlet chamber;

[0049] 13. Rotor; 131. Sliding vane;

[0050] 1311. Arc-shaped section; 1312. Spring groove; 1313. Pressure relief groove;

[0051] 1314. Connecting hole; 1315. Sealed cavity;

[0052] 14. Discharge chamber; 15. Discharge outlet; 16. Conveying gap;

[0053] 2. Connecting section; 21. Skeleton oil seal; 22. Drainage hole;

[0054] 3. Pump shaft; 31. Shaft end seal; 32. Pressure relief hole;

[0055] 41. Booster pipe; 42. Parallel inlet pipe; 43. Parallel outlet pipe. Detailed Implementation

[0056] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0057] Please see Figures 1-4 In this embodiment of the invention, a long-life vane pump and a multi-purpose vane pump are provided. The pump shaft 3 is coaxially fixed to the motor shaft of the drive motor via a coupling. Multiple sets of sliding bearings are installed on the pump shaft 3, and the sliding bearings are in rotational engagement with multiple sets of working sections 1. Taking this invention as an example, two sets of working sections 1 are arranged. The two sets of working sections 1 are driven by the pump shaft 3 as a drive source and can work independently or collaboratively.

[0058] Working section 1 has an opening on one side for inserting rotor 13. Positioning steps are arranged inside working section 1 to determine the insertion depth of rotor 13. Connecting sections 2 are arranged between two adjacent working sections 1 to close the opening of working section 1, so that the working chamber of working section 1 is in a sealed state.

[0059] The working section 1 preferably has an open bottom. A distribution plate can be installed between the rotor 13 and the positioning step of the working section 1 to distribute the medium. After the rotor 13 is installed, it can be pressed into the working section 1 by the connecting section 2. The rotating disc of the rotor 13 is connected to the pump shaft 3 by a key and rotates under the drive of the pump shaft 3.

[0060] The outer ring of the rotor 13's rotating disc has radially evenly spaced sliding vane slots for mounting the vanes 131, which can slide freely radially within the slots. A spring slot 1312 is provided at the bottom of the vane 131, and a spring is installed within the spring slot 1312. The end of the spring abuts against the bottom surface of the vane slot on the rotor 13, and under the action of the spring's elastic force, the vane 131 is tightly fitted against the inner wall of the pump body in the working section 1.

[0061] The slider 131 has arc-shaped sections 1311 on both sides, and there is a gap between the arc-shaped sections 1311 and the slider groove, so that the slider 131 can rotate in the slider groove through the arc-shaped sections 1311.

[0062] The mating surface between the sliding vane 131 and the inner wall of the pump body is a plane, with both sides of the plane contacting the inner wall of the pump body to form a two-segment line seal. The sliding vane 131, through the two-segment line seal, encloses the inner wall of the pump body to form a sealing cavity 1315. In actual use, a boss can also be machined on the surface of the sliding vane 131 to form a line seal. A through hole 1314 is provided on the sliding vane 131, through which the medium enters the sealing cavity 1315 after passing through the gap between the arc-shaped section 1311 and the sliding vane groove and the through hole 1314. A spring groove 1312 for positioning the spring is provided at the bottom of the sliding vane 131, and a pressure-reducing groove 1313 is provided on the mating surface between the sliding vane 131 and the inner wall of the pump body. The through hole 1314 passes through the spring groove 1312 and the pressure-reducing groove 1313 along the axial direction of the sliding vane 131.

[0063] The radius SR of the arc segment 1311 is:

[0064]

[0065] Let b be the midpoint of any arc segment 1311, and c be the intersection of the axis of the sliding vane 131 and the inner wall of the pump body.

[0066] Where L2 is the distance from point b to point c;

[0067] L1 is the distance from the center of gravity of slider 131 to point c;

[0068] R is the maximum radius of the inner circular curve of the stator;

[0069] r is the minimum radius of the inner circular curve of the stator;

[0070] δ is the thickness of slider 131;

[0071] z represents the number of vanes 131 in the vane pump;

[0072] Q is the design flow rate of the vane pump;

[0073] n is the rotational speed of the vane pump;

[0074] B is the axial length of slider 131.

[0075] The slider tilt angle α is between 5° and 15°.

[0076] like Figure 7 As shown:

[0077] 1. The motion state of the slider in the suction section, taking the slider at position B as an example, the slider at this position is subjected to the spring force F. k The centrifugal force F experienced by the slider during rotation r and medium pressure F p F k and F rThe direction is perpendicular to the axis of the slider and away from the center; the medium pressure F p As the pump chamber volume increases, the pressure decreases, so the medium pressure at point 2 of the slide vane is less than that at point 1. The pressure in the slide vane groove is the same as that at point 1, resulting in an imbalance of forces on both sides of the slide vane, causing counterclockwise deflection. At this time, the slide vane tilt angle is negative, and under the combined force of the three forces, both ends of the slide vane can fit tightly against the inner wall of the pump body. When the slide vane moves from position B to position C, F k and F r The sliding distance of the vane increases with the increase of the sliding distance, thus ensuring the reliability of the double-end sealing of the vane throughout the entire suction section.

[0078] 2. The motion state of the vane in the transition section from the suction section to the discharge section, taking the vane at position C as an example, at this time, position 1 of the vane is in the low-pressure zone, and position 2 is in the high-pressure zone, and the medium pressure F at position 2 of the vane end in the high-pressure zone is... p The position of the vane should be greater than 1 point on the low-pressure side, causing the vane to tilt counterclockwise. Since the inner wall of the pump body is symmetrical at this point, the vane will only be in contact with the inner wall of the pump body at 2 points, resulting in a single-contact sealing state. At the same time, due to the self-rotation of the vane, the side of the vane will not come into contact with the inner groove surface of the rotor, thus avoiding friction between the side of the vane and the inner groove surface of the rotor. This solves the problem of large side friction in the transition section of traditional long strip vanes and extends the service life of the vane.

[0079] 3. The motion state of the vane in the discharge section, taking the vane at position D as an example, is basically the same as that in the suction section, except for the medium pressure F. p The magnitude and direction differ, and the medium pressure F p As the pump cavity volume decreases, the medium pressure at point 2 of the vane increases, so the pressure at point 1 of the vane is greater than that at point 2 of the vane. The pressure in the vane groove is the same as that at point 2 of the vane, which causes the vane to deflect clockwise. At this time, the vane tilt angle is positive, and under the action of various external forces, both ends of the vane can be tightly fitted with the inner wall of the pump body, which is a double-end face seal with high sealing reliability.

[0080] 4. The motion state of the sliding vane in the transition section from the discharge section to the suction section, taking the sliding vane at position A as an example, at this time, point 1 of the sliding vane is in the high-pressure zone, and point 2 of the sliding vane is in the low-pressure zone. The medium pressure F on point 1 of the sliding vane in the high-pressure zone is... p The sliding vane needs to be positioned at two points higher than the low-pressure area, causing it to tilt clockwise. Since the pump body wall is symmetrical in this area, the sliding vane will only be in contact with the pump body wall at one point, resulting in a single-contact sealing state. At the same time, due to the self-rotation of the sliding vane, the side of the sliding vane will not come into contact with the inner groove surface of the rotor, thus avoiding friction between the side of the sliding vane and the inner groove surface of the rotor and extending the service life of the sliding vane.

[0081] It can be seen that the new type of vane reciprocates within the vane groove while also rotating around its own center. Its inclination angle changes with the force state of the vane at different positions, thus ensuring that the vane will not get stuck or wedged at any position. Secondly, due to the unique design of the vane, it has a dual sealing function at the pump body's suction and discharge sections, enhancing sealing reliability. Finally, it solves the problem of high side friction of traditional vanes under pressure change conditions in high-pressure-low-pressure and low-pressure-high-pressure zones, greatly extending the service life of the vane and impeller rotor.

[0082] like Figures 8-9 To compare the stress on the sealing end faces of the sliding plate of the present invention and the conventional sliding plate, static strength analysis was performed on both. The load boundary conditions were the same. It can be seen that the present invention, by reasonably setting the radius of the arc segment, allows the sliding plate to rotate slightly within the optimal range, making the stress values ​​on the two sealing end faces of the sliding plate much smaller than those of the conventional sliding plate, thereby reducing the wear of the end faces and improving the service life of the sliding plate.

[0083] The rotating disc, the two sets of sliding vanes, and the inner wall of the working section 1 form a conveying gap 16, through which the medium can pass. The working section 1 is provided with an inlet 11 and an outlet 15. The suction chamber 12 in the working section 1 is connected to the suction inlet 11, and the discharge chamber 14 in the working section 1 is connected to the outlet 15. After the medium enters the suction chamber 12 through the suction inlet 11, it enters the conveying gap 16 of the rotor 13. Under the rotational conveying of the rotor 13, it is discharged outward from the outlet 15 through the discharge chamber 14.

[0084] The above are just the common structures of vane pump rotors. In actual use, the structure of rotor 13 can be adapted to other existing rotor structures.

[0085] Two sets of skeleton oil seals 21 are arranged inside the connecting section 2. The two sets of skeleton oil seals 21 are coaxially fixed on the pump shaft 3. The two sets of skeleton oil seals 21 are symmetrically arranged and abut against each other to prevent the medium in the working section 1 from flowing out through the gap between the working section 1 and the pump shaft 3, and to prevent the medium from flowing between the two working sections 1. O-rings are arranged at the contact surface between the working section 1 and the connecting section 2 to prevent the medium from leaking outward.

[0086] The connecting section 2 can also be arranged with a single-sided opening to accommodate two sets of skeleton oil seals 21. Preferably, it has a bottom opening. After the skeleton oil seals 21 are inserted, the two skeleton oil seals 21 are pressed and fixed by the working section 1. A drainage hole 22 is provided radially on the connecting section 2. The drainage hole 22 communicates with the contact surface of the two sets of skeleton oil seals 21, thereby allowing the leakage of the medium to drain.

[0087] The opening of the bottom working section 1 is sealed by the pump cover, and the pump cover is fastened to each working section 1 and each connecting section 2 by bolts.

[0088] A sealing cavity is provided in the uppermost working section 1, and a shaft end seal 31 is installed in the sealing cavity to prevent medium leakage. The shaft end seal 31 is preferably a skeleton oil seal. A pressure relief hole 32 is provided in the working section 1, which connects the sealing cavity and the discharge cavity 14 of the working section 1. Since the discharge cavity 14 is a high-pressure cavity, the high-pressure medium can be led to the shaft end seal 31 through the pressure relief hole 32, and then flow back to the pump cavity of the working section 1 through the gap between the pump shaft 3 and the sliding bearing. This prevents outside air from entering the working section 1 and lubricates the sliding bearing.

[0089] Taking two sets of pumps arranged in working section 1 as an example, after the sliding vane pumps are installed, they can enter the following three working states depending on different operating conditions:

[0090] like Figure 2 As shown, in the first working state, working section 1 can be used independently or connected to different media sources, with N sets of working sections 1 corresponding to N sets of media sources. It can simultaneously transport multiple different media, pumping different media from different locations to different locations to achieve proportional media transport. Alternatively, it can pump different media from different locations to the same location to achieve proportional media mixing; or it can pump the same media from the same location to different locations to achieve proportional media distribution. The flow rate ratio can be achieved by different configurations of the pump casing eccentricity and the axial length of the rotor impeller.

[0091] like Figure 3 As shown, in the second operating state, each operating section 1 is connected to the same medium source through parallel inlet pipes 42, and the outlets 15 of each operating section 1 are connected in parallel through parallel outlet pipes 43 to discharge the medium together. At this time, the pumping flow rate is the sum of the individual pumping flow rates of each operating section 1, and the pumping medium pressure is the same as the group with the larger individual pumping medium pressure of each operating section 1. This operating state is mainly suitable for high flow rate and medium pressure applications.

[0092] like Figure 4 As shown, in the third working state, the inlet 11 of the first working section 1 is connected to the medium source, and the outlet 15 of the first working section 1 is connected to the inlet 11 of the next working section 1 through the booster pipe 41, thereby continuously pressurizing the medium during transportation, and finally discharging it outward through the outlet 15 of the last working section 1. The pumping flow rate remains constant throughout the transportation process, while the pressure continuously increases; this working state is mainly suitable for high-pressure, low-flow-rate applications.

[0093] During use, flow meters, temperature sensors, and pressure sensors can be installed on the booster pipe 41, parallel inlet pipe 42, and parallel outlet pipe 43 to monitor the conveying status of the medium under different conditions in real time, thereby adjusting the operating parameters of the vane pump in real time.

[0094] The basic principles of this application have been described above with reference to specific embodiments. However, it should be noted that the advantages, benefits, and effects mentioned in this application are merely examples and not limitations, and should not be considered as essential features of each embodiment of this application. Furthermore, the specific details disclosed above are for illustrative and facilitative purposes only, and are not limitations. These details do not limit the application to the necessity of employing the aforementioned specific details for implementation.

[0095] The block diagrams of devices, apparatuses, devices, and systems involved in this application are merely illustrative examples and are not intended to require or imply that they must be connected, arranged, or configured in the manner shown in the block diagrams. As those skilled in the art will recognize, these devices, apparatuses, devices, and systems can be connected, arranged, and configured in any manner. Words such as “comprising,” “including,” “having,” etc., are open-ended terms meaning “including but not limited to,” and are used interchangeably with them. The terms “or” and “and” as used herein refer to the terms “and / or,” and are used interchangeably with them unless the context clearly indicates otherwise. The term “such as” as used herein refers to the phrase “such as but not limited to,” and is used interchangeably with it.

Claims

1. A long-life slider, characterized in that, The sliding vane (131) has arc-shaped sections (1311) on both sides, and there is a gap between the arc-shaped sections (1311) and the sliding vane groove, so that the sliding vane (131) can rotate in the sliding vane groove through the arc-shaped sections (1311). There are at least two line seals between the sliding vane (131) and the inner wall of the pump body, so that the sliding vane (131) and the inner wall of the pump body can be enclosed to form a sealed cavity (1315). The radius of the arc segment (1311) SR for: Using the midpoint of any arc segment (1311) as b The intersection of the axis of the sliding vane (131) and the inner wall of the pump body is... c ; in, L 2 for b Click c Distance between points; L 1 For the slider (131) center of gravity to c Distance between points; R The maximum radius of the inner circular curve of the stator; r The minimum radius of the inner circular curve of the stator; δ The thickness of the slider (131); z The number of vanes (131) in the vane pump; Q This refers to the design flow rate of the vane pump. n The rotational speed of the vane pump; B y is the axial length of the slider (131).

2. The long-life slider according to claim 1, characterized in that, The mating surface between the sliding vane (131) and the inner wall of the pump body is a plane, and the two sides of the plane contact the inner wall of the pump body to form a two-segment line seal; a through hole (1314) is provided on the sliding vane (131), and the medium enters the sealing cavity (1315) after passing through the gap between the arc section (1311) and the sliding vane groove and the through hole (1314).

3. A long-life slider according to claim 2, characterized in that, The bottom of the slide (131) is provided with a spring groove (1312) for positioning the spring, and a pressure relief groove (1313) is provided on the mating surface between the slide (131) and the inner wall of the pump body. The connecting hole (1314) passes through the spring groove (1312) and the pressure relief groove (1313) in sequence along the axial direction of the slide (131).

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