Double-end-cover axial variable vane pump

Abstract

The invention discloses a double-end-cover axial variable vane pump which comprises a pump body, a transmission shaft is coaxially arranged in an inner cavity of the pump body and extends out of one side of the pump body, the other side of the pump body is sealed through an upper pump cover, a driving disc is coaxially and integrally formed on the transmission shaft and located in the pump body, and a plurality of sets of vanes are evenly arranged on the driving disc in a clearance fit mode along the circumference. A stator is coaxially fixed to an inner cavity of the pump body, the transmission shaft is matched with the stator through the pump body for axial limiting, the outer ring of the stator is slidably sleeved with a pressing cylinder, the pressing cylinder is in clearance fit with the inner wall of the pump body, and the distance between the pressing cylinder and the driving disc is adjustable. According to the vane pump, on the basis of solving the problems of hydraulic impact, cavitation, extra pressure of a vane root cavity and flow pulsation in the flow distribution process, the maximum lead between the vane and the stator is changed through vertical movement of the pressing cylinder so as to control the suction amount and the discharge amount of oil, and the vane pump has the advantages of no flow distribution, low pulsation, low noise, variable quantity and the like.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic transmission technology and involves the innovative design of the structure and working principle of vane pumps. It proposes a double-end-cover axial variable vane pump, which fills the gap in the traditional vane pump spectrum. It can be widely used in equipment fields such as automobiles, construction machinery, metallurgy, mining, marine, shipbuilding, aerospace, and aviation. It has the advantages of no flow distribution, low pulsation, low noise, variable displacement, and no limitation by centrifugal force. It can also work well even in low-speed environments. Background Technology

[0002] As the load pressure increases, the flow and pressure pulsation in the vane root chamber of existing vane pumps increases, exacerbating impact vibration and head clearance leakage during vane movement. Furthermore, with increasing speed and pressure, hydraulic shock and cavitation during oil distribution and sealing processes intensify. In addition, vane pumps require high speeds to ensure sufficient centrifugal force for the vanes to adhere tightly to the stator surface, making them unsuitable for low-speed operation. Therefore, to address these issues, patent CN116928091A proposes a novel axial vane pump structure that eliminates the distribution structure and vane root chamber, resolving the additional pressure and flow pulsation problems caused by the vane root chamber and eliminating hydraulic shock and cavitation during distribution. To further meet engineering applications and enrich its application scenarios, this invention, based on patent CN116928091A, proposes a novel structure and implementation method for a double-end-cap axial variable vane pump. This pump offers advantages such as variable displacement, no distribution, low pulsation, low noise, and no centrifugal force limitations, filling a gap in the vane pump market and further enriching its application scenarios. Summary of the Invention

[0003] To address the shortcomings of existing technologies, this invention provides a double-end-cover axial variable vane pump. This vane pump solves the problems of hydraulic shock, cavitation, additional pressure in the vane root chamber, and flow pulsation during the flow distribution process. It controls the intake and discharge of oil by changing the maximum lead between the vanes and the stator through the up-and-down movement of the pressure cylinder. This structure has the advantages of no flow distribution, low pulsation, low noise, variable displacement, and no limitation by centrifugal force.

[0004] A double-end cap axial variable vane pump includes a pump body. A drive shaft is coaxially mounted in the inner cavity of the pump body, extending out from one side of the pump body. The other side of the pump body is sealed by an upper pump cover. A drive disc is integrally formed coaxially on the drive shaft within the pump body. Multiple sets of vanes are uniformly spaced along the circumference of the drive disc. The vanes are axially supported by compression springs. A stator is coaxially fixed in the inner cavity of the pump body. The drive shaft is axially limited by the cooperation of the pump body and the stator. A pressure cylinder is slidably sleeved on the outer ring of the stator. The pressure cylinder is spaced with the inner wall of the pump body and the distance between it and the drive disc is adjustable. One side of the stator and the pressure cylinder together form a continuous curved surface for slidingly supporting the top profile of the vanes. The pump body, drive disc, vanes, drive shaft, stator, and pressure cylinder form a cavity. The stator is symmetrically provided with an oil discharge groove and an oil suction groove communicating with the cavity, and an oil discharge pipe and an oil suction pipe communicating with the oil discharge groove and the oil suction groove, respectively.

[0005] As a preferred embodiment of the above technical solution, the surface of the stator communicating with the cavity includes two sets of symmetrically arranged helical surfaces. The oil drain groove and the oil suction groove are respectively located in one set of the helical surfaces. One side of the two sets of helical surfaces is connected by an oil cover on the stator that is always in contact with the drive disc surface, and the other side is disconnected. The resulting disconnected section penetrates the stator axially and forms a sliding positioning groove. The disconnected section is slidably filled by the pressure cylinder. During the rotation of the blade, its top profile is always in contact with the continuous curved surface line formed by the stator and the pressure cylinder in the cavity.

[0006] As a preferred embodiment of the above technical solution, the pressure cylinder is provided with a guide block that cooperates with the sliding positioning groove, and the guide block is flush with the edge of the pressure cylinder.

[0007] As a preferred embodiment of the above technical solution, the distance between the pressure cylinder and the drive disc is adjusted by a fine-tuning mechanism. The fine-tuning mechanism includes a second compression spring, which is coaxially disposed between the pressure cylinder and the stator. A sliding top column abuts against the other side of the pressure cylinder. The sliding top column is slidably connected to the upper pump cover on the same axis. A top column rotating shaft is threadedly connected to the other side of the sliding top column.

[0008] As a preferred embodiment of the above technical solution, a protective cover is coaxially fixed to the outer side of the upper pump cover, and the protective cover is used to axially support the rotating shaft of the top column.

[0009] As a preferred embodiment of the above technical solution, the stator is restricted to rotate and move axially by a stator fixing component. The stator fixing component includes a positioning block and a positioning pin. The positioning block is fixed to the side wall of the stator by bolts. The inner wall of the pump body is provided with a fixing positioning groove along the axial direction. The positioning block restricts the rotation of the stator. The positioning pin is arranged in parallel with the positioning block in the fixing positioning groove. The two sides of the positioning pin abut against the positioning block and the upper pump cover, respectively, to restrict the axial movement of the stator.

[0010] As a preferred embodiment of the above technical solution, the front and rear sides of the drive disk are uniformly provided with blade grooves and limiting grooves for positioning the blades and the compression springs, and the blade grooves and limiting grooves are partially overlapped.

[0011] As a preferred embodiment of the above technical solution, the side of the drive disk away from the blade is sealed by the drive shaft end cover, one end of the compression spring abuts against the drive shaft end cover, and the side wall of the drive disk is provided with an acirculation groove that connects all the blade grooves. The acirculation groove is located at the root of the blade groove and is used to balance the air pressure in the multiple blade root cavities formed by the drive shaft end cover, drive disk, drive shaft, blades and pump body.

[0012] As a preferred embodiment of the above technical solution, an oil seal is provided between the drive shaft and the pump body, and the oil seal is pressed together by the lower pump cover.

[0013] As a preferred embodiment of the above technical solution, a limiting post for positioning the second compression spring is coaxially provided on the top surface of the inner cylinder.

[0014] Compared with the prior art, the beneficial effects of the present invention are as follows: 1. A novel axial variable displacement vane pump structure is proposed, in which the vane motion is changed from radial to axial, breaking through the traditional vane pump structure and further enriching and filling the gap in the vane pump spectrum.

[0015] 2. A novel variable displacement structure for an axial variable vane pump is proposed. Its principle is to change the maximum lead between the vane and the stator, so that the axial variable vane pump can accurately control the amount of oil sucked in and discharged, and has a wide range of applications.

[0016] 3. The distribution and sealing structures have been eliminated, which will prevent hydraulic shock, cavitation and cavitation phenomena in the distribution area. The blade root chamber has been optimized and replaced with a compression spring at the bottom of the drive disc to provide elasticity. A circulation groove is used to dynamically adjust the output pressure and flow pulsation caused by the volume change of the blade root chamber.

[0017] 4. In the proposed axial variable vane pump, the stator and vanes are in line contact, while the vanes and the inner wall of the pump body and the vanes and shaft are in surface contact. The vanes, stator, pressure cylinder, drive disc, and pump body together form a closed chamber. By changing the volume of the chamber, the high-pressure and low-pressure chambers are cyclically changed, thereby completing the oil suction and discharge actions.

[0018] 5. The designed stator and pressure cylinder mating surfaces are continuous and smooth, allowing the blades to operate relatively smoothly between the stator and pressure cylinder with low noise. The compression spring provides elastic force to the pair of blades, keeping them in close contact with the stator and pressure cylinder surfaces. No initial velocity or centrifugal force is required, and the axial variable vane pump can also work well at low speeds.

[0019] 6. Axial variable vane pumps can adjust the oil flow rate, and without the radial sliding distance of vanes and complex flow distribution structure, they are easy to miniaturize. Attached Figure Description

[0020] Figure 1 This is a cross-sectional view of the overall structure of the present invention.

[0021] Figure 2 This is a sectional view of the drive shaft.

[0022] Figure 3 This is a schematic diagram of the drive shaft.

[0023] Figure 4 This is a schematic diagram of the blade structure.

[0024] Figure 5 This is a schematic diagram showing the position of the blades between the pump body and the drive.

[0025] Figure 6 This is a schematic diagram of the stator structure.

[0026] Figure 7 This is a top view of the stator.

[0027] Figure 8 This is a schematic diagram of the pressure cylinder.

[0028] Figure 9 This is a structural schematic diagram of the stator fixing component.

[0029] Figure 10 This is a schematic diagram of the pump body.

[0030] Figure 11 This is a schematic diagram of the suction and discharge chambers of a 9-blade axial variable vane pump during one cycle, as disclosed in an embodiment of the present invention.

[0031] The attached diagram is labeled as follows: 1-Pump body, 2-Drive shaft, 3-Upper pump cover, 4-Drive disc, 5-Blade, 6-Compression spring one, 7-Stator, 8-Pressure cylinder, 9-Oil drain groove, 10-Oil suction groove, 11-Oil drain pipe, 12-Oil suction pipe, 13-Helical surface, 14-Oil cover, 15-Sliding positioning groove, 16-Guide block, 17-Compression spring two, 18-Sliding top column, 19-Top column rotation shaft, 20-Cover, 21-Positioning block, 22-Positioning pin, 23-Fixed positioning groove, 24-Blade groove, 25-Limiting groove, 26-Drive shaft end cover, 27-Circulation groove, 28-Oil seal, 29-Lower pump cover, 30-Limiting column. Detailed Implementation

[0032] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, 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, 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.

[0033] The present invention will now be described in further detail with reference to the accompanying drawings: like Figures 1 to 10 The illustrated double-end cap axial variable vane pump includes a pump body 1. A drive shaft 2 is coaxially mounted within the pump body 1, extending from one side of the pump body 1. The other side of the pump body 1 is sealed by an upper pump cover 3. A drive disc 4 is integrally formed coaxially within the pump body 1 on the drive shaft 2. Multiple sets of vanes 5 are evenly spaced along the circumference of the drive disc 4. The vanes 5 are axially supported by compression springs 6. A stator 7 is coaxially fixed within the pump body 1. The drive shaft 2 is connected to the pump body 1 and the stator 7. Axial limiting is provided. The outer ring of the stator 7 is slidably fitted with a pressure cylinder 8. The pressure cylinder 8 is clearance-fitted with the inner wall of the pump body 1 and the distance between it and the drive disk 4 is adjustable. One side of the stator 7 and the pressure cylinder 8 together form a continuous curved surface for sliding support of the top profile of the blade 5. The pump body 1, drive disk 4, blade 5, transmission shaft 2, stator 7 and pressure cylinder 8 form a cavity. The stator 7 is symmetrically provided with an oil discharge groove 9 and an oil suction groove 10 communicating with the cavity, and an oil discharge pipe 11 and an oil suction pipe 12 communicating with the oil discharge groove 9 and the oil suction groove 10 respectively.

[0034] In this embodiment, the surface of the stator 7 that communicates with the cavity includes two sets of symmetrically arranged helical surfaces 13. The oil drain groove 9 and the oil suction groove 10 are respectively located in one set of the helical surfaces 13. One side of the two sets of helical surfaces 13 is connected by an oil cover 14 on the stator 7 that is always in contact with the surface of the drive disk 4. The other side is disconnected, and the resulting disconnected section penetrates the stator 7 axially and forms a sliding positioning groove 15. The disconnected section is slidably filled by the pressure cylinder 8. During the rotation of the blade 5, its top profile is always in contact with the continuous curved surface line formed by the stator 7 and the pressure cylinder 8 in the cavity.

[0035] In this embodiment, the pressure cylinder 8 is provided with a guide block 16 that cooperates with the sliding positioning groove 15, and the guide block 16 is flush with the edge of the pressure cylinder 8.

[0036] In this embodiment, the distance between the pressure cylinder 8 and the drive disc 4 is adjusted by a fine-tuning mechanism. The fine-tuning mechanism includes a second compression spring 17, which is coaxially disposed between the pressure cylinder 8 and the stator 7. A sliding top column 18 abuts against the other side of the pressure cylinder 8. The sliding top column 18 is slidably connected to the upper pump cover 3 on the same axis. A top column rotating shaft 19 is threadedly connected to the other side of the sliding top column 18.

[0037] In this embodiment, a protective cover 20 is coaxially fixed to the outer side of the upper pump cover 3, and the protective cover 20 is used to axially support the rotating shaft 19 of the top column.

[0038] In this embodiment, the stator 7 is restricted to rotate and move axially by a stator fixing component. The stator fixing component includes a positioning block 21 and a positioning pin 22. The positioning block 21 is fixed to the side wall of the stator 7 by bolts. The inner wall of the pump body 1 is provided with a fixing positioning groove 23 along the axial direction. The positioning block 21 restricts the rotation of the stator 7. The positioning pin 22 is arranged in parallel with the positioning block 21 in the fixing positioning groove 23. The two sides of the positioning pin 22 abut against the positioning block 21 and the upper pump cover 3 respectively, in order to restrict the axial movement of the stator 7.

[0039] In this embodiment, the front and rear sides of the drive disk 4 are uniformly provided with blade grooves 24 and limiting grooves 25 for positioning the blade 5 and the compression spring 6, and the blade grooves 24 and limiting grooves 25 are partially overlapped.

[0040] In this embodiment, the side of the drive disk 4 away from the blade 5 is sealed by the drive shaft end cover 26. One end of the compression spring 6 abuts against the drive shaft end cover 26. The side wall of the drive disk 4 is provided with an annular groove 27 that connects all the blade grooves 24. The annular groove 27 is located at the root of the blade groove 24 and is used to balance the air pressure in the multiple blade root cavities formed by the drive shaft end cover 26, drive disk 4, drive shaft 2, blade 5 and pump body 1.

[0041] In this embodiment, an oil seal 28 is provided between the drive shaft 2 and the pump body 1, and the oil seal 28 is pressed by the lower pump cover 29.

[0042] In this embodiment, a limiting post 30 for positioning the compression spring 17 is coaxially provided on the inner top surface of the pressure cylinder 8.

[0043] Specifically, the main components of the axial vane pump are non-standard parts, which need to be designed independently, taking into account the fit between the components, and are made of corrosion-resistant, high-hardness materials through high-precision machining.

[0044] The cavity structure enables the pump to perform oil suction and discharge functions. During the rotation of the drive shaft 2, the volume of the cavity formed by the pump body 1, drive disc 4, blade 5, drive shaft 2, stator 7 and pressure cylinder 8 changes periodically, forming local high pressure and low pressure. In addition, the volume of the root cavity of a single blade formed by the drive shaft end cover 26, drive disc 4, drive shaft 2, blade 5 and pump body 1 also changes periodically, and is depressurized by the circulation groove 27 to eliminate the pressure caused by the change of the blade root cavity.

[0045] During the rotation of the blades 5 driven by the drive shaft 2, the cavity forms an oil suction chamber and an oil discharge chamber. When the pressure cylinder 8 stops moving, the volume of the cavity changes with the rotation of the blades 5. Furthermore, during rotation, the contact tangent between the top profile of the blades 5 and the continuous curved surface formed by the stator 7 and the pressure cylinder 8 is constantly changing, effectively reducing wear and extending the service life of the blades 5. The continuous curved surface formed by the stator 7 and the pressure cylinder 8 includes a lower sector surface (MQTP is matched by the pressure cylinder sector surface), an upper helical surface (MNRQ), an upper sector surface (RNOS), and a lower helical surface (SOPT), as shown below. Figure 7 As shown. The upper fan-shaped surface (RNOS) in the stator 7 forms a sealing oil area with the drive disk 4, blocking the passage of oil. The top profile surface of the blade 5 forms a line contact with the curved surface of the stator 7 and the pressure cylinder 8, and together with the inner wall of the pump body 1, the drive shaft 2, the drive disk 4, the pressure cylinder 8, the stator 7 and the blade 8, they form a sealed cavity.

[0046] Blade root cavity: In the blade groove 24 of the drive disc 4, under the action of the compression spring 6, the blade 5 reciprocates axially. It has a clearance fit with the blade groove 24 of the drive disc 4, and the volume of the resulting blade root cavity changes periodically. Pressure is released by the annular groove 27, eliminating the pressure generated by the changes in the blade root cavity. Furthermore, because the blade 5 rotates at high speed around its axis, to achieve sufficient lubrication and reduce friction, the inner circular surface (CDHG) of the blade 5 and the shaft of the drive shaft 2, and the outer circular surface (ABFE) of the blade 5 and the inner wall of the pump body 1, have a clearance fit. Figure 5 As shown.

[0047] Sealing structure: The sealing ring, combined sealing gasket, flat-end set screw and other structures added to prevent oil leakage from the assembly gap of the lower end cover 29, the upper end cover 3 and the oil drain pipe 11 and the oil suction pipe 12 are conventional technical means in this field and will not be described in detail here.

[0048] Support structure: Bearings and other components installed inside the pump body 1, which support the rotation of the drive shaft 2.

[0049] The working principle of the fine-tuning mechanism is as follows: In order to achieve the variable, the high-torque low-speed motor reverses or rotates forward to drive the reducer. The reducer drives the rotating shaft 19 of the top column, so that the sliding top column 18 moves up and down slowly, thereby driving the pressure cylinder 8 to rise or fall, changing the maximum lead between the blade 5 and the stator 7, thereby controlling the intake and discharge of oil.

[0050] like Figure 11 As shown, the working process of this axial variable vane pump is as follows: The number of blades in an axial variable displacement vane pump is related to the sealing zone angle (the upper and lower sector surfaces of the stator). Taking a sealing zone angle of 45° and a number of blades of 9 as an example, the angle between two adjacent blades is 40°. During one revolution of the drive shaft 2, the area between two blades undergoes four processes (157.5°~202.5° is the RNOS transition zone; 337.5°~22.5° is the MQTP transition zone; 22.5°~157.5° is the right-hand helical surface, the area containing the suction chamber; 202.5°~337.5° is the left-hand helical surface, the area containing the discharge chamber): 1. One sealing process: The chamber formed by the two blades 5 is completely located in the MQTP transition zone, at which point the sealing chamber volume is at its maximum. There are four suction chambers, four discharge chambers, and one sealing chamber. As the blades 5 rotate, the sealing chambers within the fan-shaped surface (RNOS transition zone) on the stator 7 turn towards the suction chambers, increasing their volume. Oil is drawn from the suction port of the stator 7, and the oil is distributed to the four suction chambers via the suction groove 10 on the stator 7. Simultaneously, as the blades 5 rotate, the discharge chamber volume decreases, and oil is forced from the discharge groove 9 of the stator 7 into the discharge port of the stator 7, passing through the discharge channel and finally exiting the axial variable vane pump. Simultaneously, as the blades 5 rotate, the discharge chamber gradually turns towards the upper fan-shaped surface (RNOS transition zone) and becomes a new sealing chamber.

[0051] 2. Oil Discharge Process: As the two blades rotate, they turn to the 202.5°~337.5° oil discharge chamber. At this time, part of the chamber formed by the two blades is located in the MQTP transition zone, and part is located in the 202.5°~337.5° oil discharge chamber. With continued rotation, the area formed by the two blades is completely located in the 202.5°~337.5° oil discharge chamber. Continuing to rotate, part of the chamber formed by the two blades is located in the 157.5°~202.5° RNOS transition zone, and part is still located in the oil discharge chamber. As the blades rotate, the volume of the oil discharge chamber in the previous process gradually compresses and decreases, discharging oil into the oil discharge groove 9 of the stator 7. Meanwhile, the sealing oil chamber blades 5 between the lower fan-shaped surface (MQTP transition zone) of the stator 7 are about to enter the oil discharge chamber. At this time, there are four oil suction chambers, four oil discharge chambers, and one sealing oil chamber. As the blades rotate, the volume of the oil suction chambers continues to gradually increase, absorbing oil. The volume of the oil discharge chambers decreases, discharging oil.

[0052] 3. Secondary oil sealing process: The chamber formed by the two blades 5 is completely located in the 157.5°~202.5° RNOS transition zone. At this time, the volume of the oil sealing chamber in the two-blade area is 0, which is the minimum value. As the blades 5 rotate, they emerge from the lower fan-shaped surface (MQTP transition zone) of the stator 7, gradually forming a new oil discharge chamber. At this time, there are four oil suction chambers, four oil discharge chambers, and one oil sealing chamber. As the blades 5 rotate, the volume of the oil suction chamber gradually increases, absorbing oil. Meanwhile, the volume of the oil discharge chamber decreases, discharging oil, and gradually turning towards the upper fan-shaped surface (RNOS transition zone) of the stator 7 to form a new oil sealing chamber.

[0053] 4. Oil Suction Process: As the two blades rotate, they turn to the 22.5°~157.5° oil suction chamber. At this time, part of the chamber formed by the two blades is located in the RNOS transition zone, and part is located in the 22.5°~157.5° oil suction chamber. With continued rotation, the area formed by the two blades is completely located in the 22.5°~157.5° oil suction chamber. With further rotation, part of the chamber formed by the two blades is located in the 337.5°~22.5° MQTP transition zone, and part remains in the oil suction chamber. As the blades rotate, the volume of the oil suction chamber from the previous process gradually compresses and increases, drawing oil from the oil discharge groove 10 of the stator 7. Meanwhile, the sealing oil chamber blades 5 between the fan-shaped surfaces (RNOS transition zone) on the stator 7 are about to enter the oil suction chamber. At this point, there are four oil suction chambers, four oil discharge chambers, and one sealing oil chamber. As the blades rotate, the volume of the oil suction chamber continues to gradually increase, absorbing oil. The volume of the oil discharge chamber decreases, discharging oil.

[0054] This cycle repeats continuously, allowing for the constant absorption and removal of oil.

[0055] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A double-cased axial variable vane pump characterized by: The pump body is provided with a transmission shaft coaxially arranged in the inner cavity of the pump body, the transmission shaft extends from one side of the pump body, the other side of the pump body is sealed by an upper pump cover, a driving disc is integrally formed on the transmission shaft coaxially in the pump body, a plurality of groups of blades are uniformly and gap-fitted on the driving disc in the circumferential direction, the blades are axially supported by a compression spring, a stator is fixed coaxially in the inner cavity of the pump body, the transmission shaft is axially limited by the cooperation of the pump body and the stator, a pressing cylinder is slidingly sleeved on the outer ring of the stator, the pressing cylinder is gap-fitted with the inner wall of the pump body and the distance between the pressing cylinder and the driving disc is adjustable, the stator and one side of the pressing cylinder jointly form a continuous curved surface for slidingly supporting the top profile of the blade, the pump body, the driving disc, the blade, the transmission shaft, the stator and the pressing cylinder enclose a containing cavity, the stator is symmetrically provided with an oil discharge groove and an oil suction groove which are communicated with the containing cavity, and an oil discharge pipe and an oil suction pipe which are respectively communicated with the oil discharge groove and the oil suction groove.

2. A double casing axial variable vane pump according to claim 1, characterized in that: The surface of the stator communicated with the containing cavity includes two groups of symmetrical spiral surfaces, the oil discharge groove and the oil suction groove are respectively arranged in one group of the spiral surfaces, one side of the two groups of the spiral surfaces is connected by an oil seal surface on the stator which is always in contact with the surface of the driving disc, the other side is disconnected and the formed disconnected cross section penetrates the stator along the axial direction and forms a sliding positioning groove, the disconnected cross section is slidingly filled by the pressing cylinder, and in the rotating process of the blade, the top profile of the blade is always in contact with the continuous curved surface formed by the stator and the pressing cylinder in the containing cavity.

3. A double casing axial variable vane pump according to claim 2, characterized in that: The pressing cylinder is provided with a guide block for cooperation with the sliding positioning groove, and the guide block is flush with the edge of the pressing cylinder.

4. A double casing axial variable vane pump according to claim 1, characterized in that: The distance between the pressing cylinder and the driving disc is adjusted by a fine adjustment mechanism, the fine adjustment mechanism includes a compression spring two, the compression spring two is coaxially arranged between the pressing cylinder and the stator, the other side of the pressing cylinder abuts against a sliding top column, the sliding top column is coaxially and slidingly connected with the upper pump cover, and the other side of the sliding top column is threadedly connected with a top column rotating shaft.

5. A double casing axial variable vane pump according to claim 4, characterized in that: The outer side of the upper pump cover is coaxially fixed with a cover, and the cover is used for axially supporting the top column rotating shaft.

6. A double casing axial variable vane pump according to claim 1, characterized in that: The stator is limited in rotation and axial movement by a stator fixing member, the stator fixing member includes a positioning block and a positioning pin, the positioning block is fixed to the side wall of the stator by bolts, the inner wall of the pump body is provided with a fixed positioning groove in the axial direction, the rotation of the stator is limited by the positioning block, the positioning pin is arranged in the fixed positioning groove parallel to the positioning block, and the two sides of the positioning pin abut against the positioning block and the upper pump cover respectively, so as to limit the axial movement of the stator.

7. A double casing axial variable vane pump according to claim 6, characterized in that: The front and rear sides of the driving disc are uniformly provided with blade grooves and limiting grooves for positioning the blades and the compression spring one in the circumferential direction, and the blade grooves and the limiting grooves are partially overlapped.

8. A double casing axial variable vane pump according to claim 7, characterized in that: The driving disc side away from the blades is sealed by a transmission shaft end cover, one end of the compression spring one abuts against the transmission shaft end cover, the driving disc side wall is provided with a circulation groove communicating with all the blade grooves, the circulation groove is arranged at the root of the blade groove, and is used for balancing the air pressure of the multiple blade root cavities enclosed by the transmission shaft end cover, the driving disc, the transmission shaft, the blades and the pump body.

9. A double casing axial variable vane pump according to claim 8, characterized in that: An oil seal is arranged between the transmission shaft and the pump body, and the oil seal is compressed by a lower pump cover.

10. A double casing axial variable vane pump according to claim 4, characterized in that: A limiting column for positioning the compression spring two is arranged coaxially on the inner top surface of the compression cylinder.

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