Confluence type pressurizing cycloid pump

Abstract

The invention discloses a confluence type pressurizing cycloid pump. The invention relates to an improvement on a cycloid internal gear pump structure. Through dislocation compensation, flow pulsation caused by volume change of a pump cavity is avoided, then output pressure is increased, and operation is stable. The high-pressure pump comprises a high-pressure pump body, a low-pressure pump body and a main shaft, the axis of an outer rotor A and the axis of an outer rotor B are arranged on one side of the main shaft, the axis of the outer rotor of the high-pressure pump is arranged on the other side of the main shaft, the axis of the outer rotor A forms an included angle of + alpha relative to the horizontal line, the axis of the outer rotor B forms an included angle of-alpha relative to the horizontal line, alpha = 360 degrees / 2N, and N is the number of teeth of an inner rotor. By the adoption of the ingenious design that the rotor is eccentrically installed, pressurization of the pump is achieved, flow pulsation caused by volume changes of a pump cavity is solved through innovative dislocation compensation, and stable flow is provided for an inlet of the high-pressure booster pump. The invention can be widely applied to the fields of new energy automobiles, wind power, air conditioners, generators, industrial production, chemical industry, petroleum, metallurgy, water treatment and the like, and is used for conveying various liquids.

Description

Technical Field

[0001] The invention relates to the technical field of positive displacement hydraulic pumps, and in particular to an improvement on the structure of a cycloid internal meshing gear pump. Background Art

[0002] At present, gear pumps generally use involute spur gears, involute spiral gears, cycloid gears, linear conjugate gears, circular arc involute circular arc gears, etc. Different types of gear pumps are designed by utilizing the meshing characteristics of the corresponding gears to complete the pumping of the medium. As the main engine equipment of the prior art develops in the direction of high power, high efficiency, and multiple working conditions, the weight, volume, efficiency, pressure, pulsation, vibration, noise, etc. of the gear pump are relatively high. Only the cycloid internal gear pump can meet the comprehensive performance of small size, high efficiency, small pulsation, strong self-priming, and low vibration and noise. However, in actual application, the cycloid internal gear pump has the problems of low pressure, small flow, and shaft misalignment. As a result, the cycloid internal gear pump of the prior art is not enough to meet the application requirements of equipment such as high-end mechanical equipment in the aviation industry, new energy vehicles, and high-power wind power.

[0003] In order to expand the application field of cycloid internal gear pumps and meet the development of industrial equipment, the pressure and flow rate of cycloid internal gear pumps need to be increased. However, due to the structural characteristics of cycloid pumps, simply increasing the pressure will lead to shaft misalignment, which will cause wear of the pump cavity rotor, vibration noise and other problems.

[0004] Therefore, how to combine its own structural characteristics to alleviate the misalignment of the shaft when increasing the pressure of the cycloid pump, thereby effectively improving the overall stability of the equipment, has become a technical problem that needs to be urgently solved in this field. Summary of the invention

[0005] In view of the above technical problems, the present invention provides a converging-type booster cycloid pump which avoids flow pulsation caused by changes in pump chamber volume through misalignment compensation, thereby achieving output pressure enhancement and running smoothly.

[0006] The technical solution of the present invention is: comprising a high-pressure pump body, a low-pressure pump body and a main shaft, wherein the low-pressure pump body comprises a pump body A and a pump body B respectively arranged on the left and right sides of the high-pressure pump body, and a connecting plate is further arranged between the pump body A and the high-pressure pump body; The pump body A is provided with a pump cavity A, and an outer rotor A and an inner rotor A are movably provided in the pump cavity A. An axial pump body A flow channel is provided at the upper part of the pump body A, and the pump body A flow channel is connected to the pump cavity A. A pump body A inlet connected to the pump body A flow channel is provided at the top of the pump body A; A through-type connecting plate flow channel is provided at the lower part of the connecting plate; The end surface of the high-pressure pump body facing the connecting plate is provided with a high-pressure pump chamber, and a high-pressure pump outer rotor and a high-pressure pump inner rotor are provided in the high-pressure pump chamber; a through-type high-pressure pump flow channel is provided in the lower part between the bottom surface of the high-pressure pump chamber and the other end surface of the high-pressure pump body, a high-pressure outlet flow channel is provided in the upper part between the bottom surface of the high-pressure pump chamber and the other end surface of the high-pressure pump body, and a high-pressure pump outlet connected to the high-pressure outlet flow channel is provided at the top of the high-pressure pump body; The pump body B is provided with a pump cavity B, an outer rotor B and an inner rotor B are movably provided in the pump cavity B, an axial pump body B flow channel is provided at the upper part of the pump body B, the pump body B flow channel is connected to the pump cavity B, and a pump body B inlet connected to the pump body B flow channel is provided at the top of the pump body B; The axes of the outer rotor A and the outer rotor B are arranged on one side of the main shaft, and the axis of the outer rotor of the high-pressure pump is arranged on the other side of the main shaft. The axis of the outer rotor A forms an angle of +α relative to the horizontal line, and the axis of the outer rotor B forms an angle of -α relative to the horizontal line, α=360° / 2N, and N is the number of teeth of the inner rotor.

[0007] Furthermore, the thickness of the inner rotor A and the inner rotor B is t, and the thickness of the high-pressure pump inner rotor is 1.5-2.0t.

[0008] Furthermore, a connecting plate flow channel drainage groove L and a connecting plate flow channel drainage groove R are respectively opened at both ends of the connecting plate flow channel.

[0009] Furthermore, sealing structures are respectively provided on both end surfaces of the connecting plate.

[0010] Furthermore, positioning shoulders are respectively provided on both end surfaces of the connecting plate.

[0011] Furthermore, a high-pressure pump body positioning step circle coaxial with the main shaft is provided at the edge of the high-pressure pump chamber for matching with the positioning shoulder on the connecting plate.

[0012] Furthermore, a positioning structure and a sealing structure are provided between the high-pressure pump body and the pump body B.

[0013] Furthermore, the pump body A, the connecting plate and the high-pressure pump body are respectively provided with respective central holes, and the pump body B is provided with a middle blind hole for accommodating the main shaft; and a sliding bearing is provided between the main shaft and each of the central holes and the middle blind hole.

[0014] The present invention realizes the pump boost by utilizing the special eccentric structure of the inner and outer rotors of the cycloid pump and adopting the ingenious design of the rotor eccentric installation. By designing the rotor eccentric angle, the front and rear misalignment compensation of the two low-pressure pump output chambers is realized, and the hydraulic oil is converged to the high-pressure pump; the innovative misalignment compensation measures solve the flow pulsation caused by the change in the volume of the pump chamber, and provide a stable flow for the inlet of the high-pressure booster pump. By designing the parameters of the high-pressure booster pump rotor and the low-pressure pump rotor, and the structural layout of the two low-pressure pumps and the high-pressure booster pump, the radial force of the pump main shaft is effectively alleviated, large flow boost is achieved, and the flow pulsation is compensated auxiliaryly, which improves the overall performance and life of the pump.

[0015] The present invention can be widely used in the fields of new energy vehicles, wind power, air conditioners, generators, industrial production, chemical industry, petroleum, metallurgy, water treatment, etc., for conveying various liquids. Due to its compact structure, stable operation, low noise level, small vibration amplitude, strong self-priming ability, small flow pulsation, high volumetric efficiency, high transmission efficiency, strong viscosity and other advantages, it can ensure safety and reliability in various fields. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0017] Figure 1 is a three-dimensional exploded view of the present invention; Figure 2 It is a schematic diagram of the structure of the present invention; Figure 3 It is a schematic diagram of the structure of the pump body A in the present invention; Figure 4 yes Figure 3 Right view of; Figure 5 It is a three-dimensional schematic diagram of the connecting plate in the present invention; Figure 6 is a schematic diagram of the structure of the connecting plate of the present invention, Figure 7 yes Figure 6 Left view of Figure 8 It is a three-dimensional schematic diagram of the high-pressure pump body of the present invention; Fig. 9 It is a structural schematic diagram of the high-pressure pump body of the present invention; Fig.10 yes Fig. 9 Left view of Fig.11It is a schematic diagram of the structure of the pump body B in the present invention; Fig.12 yes Fig.11 Left view of Fig.13 The working principle of the present invention is Figure 1 ; Fig.14 yes Fig.13 Middle AA section view; Fig.15 yes Fig.13 Middle BB section view; Fig.16 yes Fig.13 Middle CC section view.

[0018] In the figure: 1 is pump body A, 11 is outer rotor A, 12 is inner rotor A, 10 is pump body A inlet, 100 is pump body A flow channel, 101 is pump cavity A, 102 is positioning step circle A, 2 is a connecting plate, 200 is a connecting plate flow channel, 2001 is a connecting plate flow channel drainage groove L, 2002 is a connecting plate flow channel drainage groove R, 201 is a positioning shoulder, 202 is a sealing groove, 3 is the high-pressure pump body, 30 is the high-pressure pump outlet, 300 is the high-pressure pump flow channel, 3001 is the high-pressure pump flow channel drainage groove L, 3002 is the high-pressure pump flow channel drainage groove R, 301 is the high-pressure pump cavity, 302 is the high-pressure outlet flow channel, 303 is the high-pressure pump body positioning shoulder, 304 is the high-pressure pump body positioning step circle, 31 is the high-pressure pump outer rotor, 32 is the high-pressure pump inner rotor, 4 is the pump body B, 40 is the pump body B inlet, 400 is the pump body B flow channel, 401 is the pump cavity B, 402 is the positioning step circle B, 41 is the outer rotor B, 42 is the inner rotor B, 5 is the main axis, In the figure, P0 is the low-pressure pump inlet pressure, P1 is the low-pressure pump outlet pressure, and P2 is the high-pressure pump outlet pressure. F1 is the radial force of the low-pressure pump outlet on the main shaft, F2 is the radial force of the high-pressure pump low-pressure confluence area on the main shaft, and F3 is the radial force of the high-pressure pump high-pressure area on the main shaft. t is the rotor thickness, O0 is the center of the main axis, O 31 is the center of the outer rotor of the high-pressure pump, O 11 is the center of the outer rotor A, O 41 is the center of the outer rotor B; Fig.13 The double-dotted arrow line in the middle indicates the flow trajectory of the fluid. Figure 13-16 The hollow arrow filled with slashes indicates the flow direction of the fluid. DETAILED DESCRIPTION

[0019] The technical solution of the present invention is further described below with reference to the accompanying drawings and through specific implementation methods.

[0020] Among them, the drawings are only used for illustrative explanations, and they only represent schematic diagrams rather than actual pictures, and should not be understood as limitations on this patent; in order to better illustrate the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of the actual product; for those skilled in the art, it is understandable that some well-known structures and their descriptions in the drawings may be omitted.

[0021] The same or similar numbers in the drawings of the embodiments of the present invention correspond to the same or similar parts; in the description of the present invention, it should be understood that if the terms "upper", "lower", "left", "right", "inner", "outer", etc. appear, the orientation or position relationship indicated is based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, the terms describing the position relationship in the drawings are only used for illustrative purposes and cannot be understood as a limitation on this patent. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

[0022] In the description of the present invention, unless otherwise clearly specified and limited, if the term "connection" or the like appears to indicate the connection relationship between components, the term should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two components or the interaction relationship between two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0023] like Figure 1-12 As shown, it includes a high-pressure pump body 3, a low-pressure pump body and a main shaft 5. The low-pressure pump body includes a pump body A1 and a pump body B4 which are respectively arranged on the left and right sides of the high-pressure pump body 3. A connecting plate 2 is also provided between the pump body A1 and the high-pressure pump body 3, so that the pump body A1, the connecting plate 2, the high-pressure pump body 3 and the pump body B4 are connected in sequence.

[0024] A pump chamber A101 is provided in the pump body A1, an outer rotor A11 and an inner rotor A12 are movably provided in the pump chamber A101, an axial pump body A flow channel 100 is provided at the upper part of the pump body A1, the pump body A flow channel 100 is connected to the pump chamber A101, and a pump body A inlet 10 connected to the pump body A flow channel 100 is provided at the top of the pump body A1; A through-type connecting plate flow channel 200 is provided at the lower part of the connecting plate 2; A high-pressure pump chamber 301 is provided on the end surface of the high-pressure pump body 3 facing the connecting plate 2, and a high-pressure pump outer rotor 31 and a high-pressure pump inner rotor 32 are provided in the high-pressure pump chamber 301; a through-type high-pressure pump flow channel 300 is provided at the lower part between the bottom surface of the high-pressure pump chamber 301 and the other end surface of the high-pressure pump body 3, a high-pressure outlet flow channel 302 is provided at the upper part between the bottom surface of the high-pressure pump chamber 301 and the other end surface of the high-pressure pump body 3, and a high-pressure pump outlet 30 connected to the high-pressure outlet flow channel 301 is provided at the top of the high-pressure pump body 3; A pump cavity B401 is provided in the pump body B4, an outer rotor B41 and an inner rotor B42 are movably provided in the pump cavity B401, an axial pump body B flow channel 400 is provided at the upper part of the pump body B4, the pump body B flow channel 400 is connected to the pump cavity B401, and a pump body B inlet 40 connected to the pump body B flow channel 400 is provided at the top of the pump body B4; The axes of the outer rotor A11 and the outer rotor B41 are arranged on one side of the main shaft 5, and the axis of the high-pressure pump outer rotor 31 is arranged on the other side of the main shaft 5. The axis of the outer rotor A11 forms an angle of +α relative to the horizontal line, and the axis of the outer rotor B31 forms an angle of -α relative to the horizontal line, α=360° / 2N, N is the number of teeth of the inner rotor.

[0025] like Figure 14-16 As shown, the present invention utilizes the meshing principle of the inner and outer gears of the cycloid pump to ensure that the centers of the inner rotor A12, the inner rotor B42 and the inner rotor 32 of the high-pressure pump are coaxial with the main shaft 5 (i.e. Figure 14-16 In the middle O0), the inlet and outlet settings are realized by installing and adjusting the eccentric position of the outer rotors of the three pump bodies. Here it is necessary to explain as follows: Each outer rotor is coaxial with the pump cavity. Figure 14-16 China-Israel 31 Indicates the center of the high-pressure pump outer rotor 31, O 11 Indicates the center of the outer rotor A11, O 41 Indicates the center of the outer rotor B41.

[0026] Axis O of outer rotor A11 11 and the axis O of the outer rotor B41 41 The high-pressure pump outer rotor 31 is located on the left side of the axis O0 of the main shaft 5. 31 On the opposite side, the hydraulic oil enters through the pump body A inlet 10 and the pump body B inlet 40 respectively, and then flows into the pump chamber A101 and the pump chamber B401 respectively through the pump body A flow channel 100 and the pump body B flow channel 400. The hydraulic oil in the pump chamber A101 and the pump chamber B401 converge into the high-pressure pump chamber 301, and then under the action of the inner and outer rotors of the high-pressure pump, the hydraulic oil converges and increases pressure and flows from the high-pressure outlet channel 302 to the high-pressure pump outlet 30, realizing two-stage oil supply.

[0027] According to the inherent meshing characteristics of gears, the present invention utilizes the relative movement between two gears of special shapes (an internal gear and an external gear) to transport fluid. The size of the meshing cavity changes periodically, resulting in unstable oil volume at the inlet of the high-pressure boost pump. Taking the inner rotor with six teeth as an example, the outer rotor A11 is offset 30° to the upper left, and the outer rotor B41 is offset 30° to the lower left, thereby realizing front and rear misalignment compensation of the two low-pressure pump output cavities, solving the flow pulsation caused by the change in the pump cavity volume, and providing a stable flow for the inlet of the high-pressure boost pump.

[0028] like Fig.13 As shown, further, the thickness of the inner rotor A12 and the inner rotor B42 is t, and the thickness of the high-pressure pump inner rotor 32 is 1.5~2.0t.

[0029] The boosting cycloid pump of the present invention adopts a two-inlet and one-outlet design method, and inputs liquid through two inlets to provide sufficient input flow for the boosting pump. The inner and outer rotors of pump body A1 and pump body B4 are exactly the same size. The inner and outer rotors of high-pressure pump body 3 are calculated according to input flow, efficiency, etc. The design parameters are the same as those of the inner and outer rotors of pump body A1 or pump body B4, but the rotor width of high-pressure pump body 3 is 1.8 times the rotor width of pump body A1 or pump body B4. The input flow of pump body A1 and pump body B4 is 2Q, and the input of high-pressure pump body 3 is 1.8Q. This design can not only alleviate the inherent flow pulsation problem of gear pumps, but also achieve a large flow of the cycloid pump during the boosting process. Each group of cycloid pumps has a high-pressure zone, and the corresponding shaft is subjected to radial force, which will cause misalignment of the shaft. The present invention can alleviate the total radial force F0 of the shaft to the greatest extent. In the present invention, according to Fig.13 As shown, the forces acting on the main shaft 5 are as follows: radial force F1 acting on the main shaft from the outlet of the low-pressure pump body A, B, radial force F2 acting on the main shaft from the low-pressure confluence area of ​​the high-pressure pump, and radial force F3 acting on the main shaft from the high-pressure area of ​​the high-pressure pump.

[0030] Taking the above-mentioned embodiment of the rotor width as an example, F2 is calculated by pressure P1 and area to get F2=1.8F1, F0=F3-(F1+F2+F1)=F3-3.8F1. This design can not only alleviate the inherent flow pulsation problem of the gear pump, but also achieve a large flow of the cycloid pump during the pressurization process; through the layout design of two low-pressure pumps and a high-pressure booster pump, the existing multi-stage cycloid pump main shaft is avoided. The upper and lower alternating force layout is avoided, and the radial force imbalance of the main shaft is alleviated. The misalignment problem, thereby maintaining a relatively stable alignment state, increasing the rotation speed of the main shaft, and reducing the vibration and leakage caused by misalignment during operation; reducing the vibration noise of the pump and improving stability.

[0031] Furthermore, a connecting plate channel drainage groove L3001 and a connecting plate channel drainage groove R3002 are respectively opened at both ends of the connecting plate channel 200, which can provide a specific flow direction for the hydraulic oil, ensure that the hydraulic oil flows more smoothly, avoid irregular turbulence of the hydraulic oil, and help improve the working efficiency and stability of the booster cycloid pump.

[0032] Furthermore, sealing grooves 202 are respectively provided on both end surfaces of the connecting plate 2 .

[0033] Furthermore, positioning shoulders 201 are respectively provided on both end surfaces of the connecting plate 2 .

[0034] Furthermore, a high-pressure pump body positioning step circle 304 coaxial with the main shaft 5 is provided at the edge of the high-pressure pump chamber 301 for matching with the positioning shoulder 201 on the connecting plate 2 .

[0035] Furthermore, a positioning structure and a sealing structure are provided between the high-pressure pump body 3 and the pump body B4.

[0036] The positioning step circle A102 is sleeved on the positioning shoulder 201 on one side of the connecting plate 2, and the positioning shoulder 201 on the other side of the connecting plate 2 is connected to the high-pressure pump body positioning step circle 304, and the high-pressure pump body positioning shoulder 303 is connected to the positioning step circle B402 to form the positioning of the booster cycloid pump.

[0037] The sealing structure at both ends of the connecting plate 2 and the sealing structure between the high-pressure pump body 3 and the pump body B4 can effectively prevent oil from leaking out of the pump body connection, ensure that the oil in the pump body can circulate in the system, reduce oil loss, maintain a stable oil volume, and prevent the normal operation of the equipment from being affected by oil leakage.

[0038] Furthermore, the pump body A1, the connecting plate 2 and the high-pressure pump body 3 are respectively provided with respective central holes, and the pump body B4 is provided with a middle blind hole for accommodating the main shaft 5; sliding bearings are provided between the main shaft 5 and the central holes and the middle blind hole.

[0039] The present invention has the following characteristics: The first is to use a booster cycloid pump to effectively increase the working pressure and flow of the existing cycloid pump during operation, thereby improving the mechanical efficiency and volumetric efficiency of the pump.

[0040] Secondly, the booster cycloid pump of the present invention can alleviate shaft misalignment, thereby improving the working stability and volumetric efficiency of the booster cycloid pump and reducing the leakage and vibration of the pump.

[0041] Third, through the eccentric design of the outer rotor, the front and rear misalignment compensation of the two low-pressure pump output chambers is achieved, the flow pulsation caused by the change of pump chamber volume is solved, and a stable flow is provided for the inlet of the high-pressure booster pump.

[0042] The present invention can effectively improve the working pressure and flow rate of the cycloid pump, reduce volume loss and gear wear, and significantly reduce vibration and noise caused by pressure pulsation, thereby generally improving the comprehensive performance of the existing gear pump and increasing its service life.

[0043] It should be noted that the above specific implementations are only preferred embodiments of the present invention and the technical principles used. Those skilled in the art should understand that various modifications, equivalent substitutions, changes, etc. can be made to the present invention based on the technical content disclosed in this application document. However, as long as these changes do not deviate from the spirit of the present invention, they should be within the scope of protection of the present invention. In addition, some terms used in the specification and claims of this application are not restrictive, but are only for the convenience of description.

Claims

1. A converging type booster cycloid pump, comprising a high-pressure pump body, a low-pressure pump body and a main shaft, characterized in that: The low-pressure pump body comprises a pump body A and a pump body B respectively arranged on the left and right sides of the high-pressure pump body, and a connecting plate is also arranged between the pump body A and the high-pressure pump body; The pump body A is provided with a pump cavity A, and an outer rotor A and an inner rotor A are movably provided in the pump cavity A. An axial pump body A flow channel is provided at the upper part of the pump body A, and the pump body A flow channel is connected to the pump cavity A. A pump body A inlet connected to the pump body A flow channel is provided at the top of the pump body A; A through-type connecting plate flow channel is provided at the lower part of the connecting plate; The end surface of the high-pressure pump body facing the connecting plate is provided with a high-pressure pump chamber, and a high-pressure pump outer rotor and a high-pressure pump inner rotor are provided in the high-pressure pump chamber; a through-type high-pressure pump flow channel is provided in the lower part between the bottom surface of the high-pressure pump chamber and the other end surface of the high-pressure pump body, a high-pressure outlet flow channel is provided in the upper part between the bottom surface of the high-pressure pump chamber and the other end surface of the high-pressure pump body, and a high-pressure pump outlet connected to the high-pressure outlet flow channel is provided at the top of the high-pressure pump body; The pump body B is provided with a pump cavity B, an outer rotor B and an inner rotor B are movably provided in the pump cavity B, an axial pump body B flow channel is provided at the upper part of the pump body B, the pump body B flow channel is connected to the pump cavity B, and a pump body B inlet connected to the pump body B flow channel is provided at the top of the pump body B; The axes of the outer rotor A and the outer rotor B are arranged on one side of the main shaft, and the axis of the outer rotor of the high-pressure pump is arranged on the other side of the main shaft. The axis of the outer rotor A forms an angle of +α relative to the horizontal line, and the axis of the outer rotor B forms an angle of -α relative to the horizontal line, α=360° / 2N, and N is the number of teeth of the inner rotor.

2. A converging-type booster cycloid pump according to claim 1, characterized in that: The thickness of the inner rotor A and the inner rotor B is t, and the thickness of the inner rotor of the high-pressure pump is 1.5-2.0t.

3. A converging-flow booster cycloid pump according to claim 1 or 2, characterized in that: A connecting plate flow channel drainage groove L and a connecting plate flow channel drainage groove R are respectively opened at both ends of the connecting plate flow channel.

4. A converging-flow booster cycloid pump according to claim 3, characterized in that: Sealing structures are also provided on both end surfaces of the connecting plate.

5. A converging-flow booster cycloid pump according to claim 3, characterized in that: Positioning shoulders are respectively provided on both end surfaces of the connecting plate.

6. A converging-flow booster cycloid pump according to claim 5, characterized in that: A high-pressure pump body positioning step circle coaxial with the main shaft is provided at the edge of the high-pressure pump chamber for matching with the positioning shoulder on the connecting plate.

7. A converging-flow booster cycloid pump according to claim 1 or 2, characterized in that: A positioning structure and a sealing structure are also provided between the high-pressure pump body and the pump body B.

8. A converging-flow booster cycloid pump according to claim 1 or 2, characterized in that: The pump body A, the connecting plate and the high-pressure pump body are respectively provided with respective central holes, and the pump body B is provided with a middle blind hole for accommodating the main shaft; a sliding bearing is provided between the main shaft and each of the central holes and the middle blind hole.

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