Gear pump for topology reconstruction of partial pressure section

Abstract

The invention discloses a partial pressure section topology reconstruction gear pump, and relates to the technical field of positive displacement gear pumps. Which comprises a pump body, a front pump cover, a rear pump cover and a main shaft, and is characterized in that the pump body is provided with a cycloid pump cavity located in the front, a gear pump cavity and a main shaft hole, the cycloid pump cavity is provided with an inlet communicated with the outside, and the gear pump cavity is provided with an outlet communicated with the outside; the pump body is further provided with a U-shaped inner flow channel communicated with the cycloid pump cavity and the gear pump cavity. A cycloid pump assembly is arranged in the cycloid pump cavity, and a gear pump assembly is arranged in the gear pump cavity; an overflow flow channel is further formed in the pump body and communicated with the U-shaped inner flow channel and the inlet, and an overflow valve is arranged on the overflow flow channel. The gear pump has the advantages of being compact in structure, stable in operation, low in noise level, small in vibration amplitude, high in self-suction capacity, small in flow pulsation, high in volume efficiency, high in transmission efficiency and the like, and the safety and reliability of operation in various fields can be ensured.

Description

Technical Field

[0001] This invention relates to the field of positive displacement gear pump technology, and more particularly to a gear pump with topological reconstruction of the pressure-sharing section. Background Technology

[0002] Among traditional gear pumps, the most widely used are external gear pumps and internal gear cycloidal pumps. External gear pumps typically employ involute spur gears, involute helical gears, cycloidal gears, linear conjugate gears, and circular arc involute gears, utilizing the meshing characteristics of corresponding gears to design different models of gear pumps for media transport. However, external gear pumps suffer from low efficiency, strong pulsation, insufficient self-priming, and high vibration and noise during operation. Internal gear cycloidal pumps, on the other hand, offer a combination of advantages including small size, high efficiency, low pulsation, strong self-priming, and low vibration and noise; however, they suffer from lower pressure, lower flow rate, and shaft misalignment issues.

[0003] As equipment now evolves towards higher power, higher efficiency, and multi-condition operation, simply using cycloidal internal gear pumps is insufficient to meet the pressure and efficiency requirements of high-end mechanical equipment in the aerospace industry, new energy vehicles, and high-power wind power equipment. Conversely, simply using external gear pumps is also insufficient to meet the pressure, vibration, and noise requirements of high-end equipment operation.

[0004] To achieve increased pressure and avoid flow pulsation, the applicant previously submitted a proposal (Publication No.: 202510317207.X, Title: A Combination Type Booster Cycloidal Pump), which achieved some success. However, in applications such as aerospace industry and high-end mechanical equipment, new energy vehicles, and high-power wind power, its working pressure, flow rate, and efficiency still have certain limitations. Summary of the Invention

[0005] To address the above-mentioned technical problems, this invention provides a gear pump with a compact structure that maximizes the balance between volume and performance to meet the matching of interstage pressures, thereby achieving topological reconfiguration of the pressure-dividing sections in a series-type boosting system.

[0006] The technical solution of this invention is: a gear pump with pressure-sharing section topology reconstruction, comprising a pump body, a front pump cover, a rear pump cover, and a main shaft, characterized in that the pump body has a cycloidal pump chamber, a gear pump chamber, and a main shaft hole located at the front. The cycloidal pump chamber has an inlet that connects to the outside, the gear pump chamber has an outlet that connects to the outside, and the pump body also has a U-shaped inner flow channel that connects the cycloidal pump chamber and the gear pump chamber. A cycloidal pump assembly is provided inside the cycloidal pump chamber, and a gear pump assembly is provided inside the gear pump chamber; An overflow channel is also provided in the pump body, which connects the U-shaped inner channel and the inlet, and an overflow valve is provided on the overflow channel.

[0007] Furthermore, the cycloidal pump assembly includes an inlet distribution plate, an outer rotor, an inner rotor, and an outlet distribution plate, wherein the outer rotor meshes with the inner rotor, and the inner rotor is connected to the main shaft.

[0008] Furthermore, the inlet distribution plate is provided with an arc-shaped through groove, the width of which gradually decreases. A side oil port is also provided on the inlet distribution plate to connect the widest part of the arc-shaped through groove to the inlet.

[0009] Furthermore, a distribution plate positioning pin hole is provided on the inner end face of the front pump cover, and a positioning pin is provided on the inlet distribution plate. The inlet distribution plate is connected to the distribution plate positioning pin hole on the inner end face of the front pump cover through the positioning pin.

[0010] Furthermore, the outlet distribution plate is provided with an arc-shaped through groove II, the width of which gradually widens. A side oil port II is also provided on the outlet distribution plate, which connects the widest part of the arc-shaped through groove II to the inlet of the U-shaped inner flow channel.

[0011] Furthermore, an outlet distribution plate positioning pin hole is provided on the bottom surface of the cycloidal pump chamber, and another positioning pin is provided on the outlet distribution plate. The outlet distribution plate is connected to the outlet distribution plate positioning pin hole on the bottom surface of the cycloidal pump chamber through the other positioning pin.

[0012] Furthermore, the rear pump cover has an "8" shaped cavity, and an "8" shaped sleeve is provided within the cavity. The "8" shaped sleeve has an upper shaft hole and a lower shaft hole. Bearing one is provided in the upper shaft hole, and bearing two is provided in the lower shaft hole. The gear pump assembly includes a driving gear and a driven gear. The driving gear is connected to the main shaft, the main shaft is movably connected to the main shaft hole in the middle, and the tail end of the main shaft is movably connected to the bearing one. The driven gear meshes with the driving gear and has a short shaft. One end of the short shaft is movably connected to the pump body, and the other end is connected to the bearing two.

[0013] Furthermore, the working displacement of the cycloidal pump assembly is Vc, the working displacement of the gear pump assembly is Vg, and the rotational speed of the main shaft is n; therefore, the flow rate of the cycloidal pump assembly is Qc = Vc × n, and the flow rate of the gear pump assembly is Qg = Vg × n. Qc≥Qg×(1+δ) In the formula, δ is the comprehensive margin coefficient for manufacturing error, leakage and changes in medium viscosity.

[0014] This invention innovatively combines an internal cycloidal gear pump unit and an external gear pump unit in series, featuring a multi-stage structure. This solves the problems of high and low pressure efficiency, size, noise, and cost associated with traditional external or internal cycloidal gear pump units. With its optimized high and low pressure operation, compact multi-stage structure, and low-cost, high-reliability design, it can be widely used in new energy vehicles, wind power, air conditioning, generators, industrial production, chemical, petroleum, metallurgy, and water treatment fields for transporting various liquid media. This invention's gear pump can be used in high and low temperature, high speed, and high pressure conditions. Compared to traditional cycloidal pumps, it offers higher operating pressure, higher speed, and lower pulsation; compared to traditional external gear pumps, it is smaller, more efficient, and has lower pulsation. This invention's gear pump boasts advantages such as compact structure, stable operation, low noise level, low vibration amplitude, strong self-priming capability, low flow pulsation, high volumetric efficiency, and high transmission efficiency, ensuring safety and reliability in various fields. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0016] Figure 1 This is a three-dimensional exploded view of the present invention; Figure 2 This is a schematic diagram of the structure of the present invention; Figure 3 This is a three-dimensional schematic diagram of the pump body in this invention. Figure 1 ; Figure 4 This is a three-dimensional schematic diagram of the pump body in this invention. Figure 2 ; Figure 5 This is a schematic diagram of the pump body in this invention; Figure 6 yes Figure 5 Sectional view of AA; Figure 7 yes Figure 5 BB section view; Figure 8 This is a three-dimensional schematic diagram of the front pump cover in this invention; Figure 9 This is a three-dimensional schematic diagram of the rear pump cover in this invention; Figure 10 This is a three-dimensional schematic diagram of the inlet / outlet distribution plate in this invention; Figure 11 This is a schematic diagram of the inlet / outlet distribution plate structure in this invention; Figure 12yes Figure 11 CC section view; Figure 13 This is a hydraulic schematic diagram of the present invention; Figure 14 This is the working principle of the invention. Figure 1 ; Figure 15 This is the working principle of the invention. Figure 2 ; Figure 16 This is a graph showing the pressure and flow rate during the operation of this invention; In the diagram: 1 is the front pump cover, 11 is the inner end face, 12 is the shaft hole, 13 is the pump body locating pin hole, 14 is the distributor plate locating pin hole, and 15 is the first sealing groove. 2 is the pump body, 201 is the inlet, 202 is the outlet, 203 is the U-shaped inner flow channel, 2031 is the inner flow channel inlet, 2032 is the inner flow channel outlet, 21 is the cycloidal pump chamber, 22 is the gear pump chamber, 23 is the main shaft hole, and 24 is the driven shaft hole. 3 is the rear pump cover, 31 is the figure-eight shaped cavity of the rear pump cover, and 32 is the second sealing groove. 4 is the main axis. 5 is the cycloidal pump assembly; 51 is the inlet distribution plate; 511 is the first arc-shaped through groove; 512 is the first side oil port; 513 is the locating pin; 52 is the outer rotor; 53 is the inner rotor; 54 is the outlet distribution plate; 541 is the second arc-shaped through groove; 542 is the second side oil port. 6 is the gear pump assembly, 61 is the drive gear, 62 is the driven gear, 63 is the figure-eight sleeve, 631 is the upper shaft hole, 632 is the lower shaft hole, 633 is the third sealing groove, 64 is the first bearing, and 65 is the second bearing. 7 is the overflow valve, and 71 is the overflow channel. M1 is the inlet of the cycloidal pump, M2 is the outlet of the cycloidal pump, N1 is the inlet of the external gear pump, and N2 is the outlet of the external gear pump. Figure 13-15 The hollow arrow indicates the direction of hydraulic fluid flow. Figure 15 Section I is the internal meshing section, section II is the inter-stage transition zone, and section III is the external meshing section. Figure 16 In the graph, ① represents the outlet pressure, ② represents the interstage pressure, ③ represents the overflow threshold, ④ represents the output flow rate, ⑤ represents the interstage flow rate, and ⑥ represents the overflow flow rate. Detailed Implementation

[0017] The following is in conjunction with the appendix Figure 1-16 The technical solution of the present invention will be further illustrated through specific embodiments.

[0018] The accompanying drawings are for illustrative purposes only and are schematic diagrams, not actual images. They should not be construed as limiting the scope of this patent. To better illustrate the embodiments of the present invention, some parts in the drawings may be omitted, enlarged, or reduced, and do not represent the actual dimensions of the product. It is understandable to those skilled in the art that some well-known structures and their descriptions may be omitted in the drawings.

[0019] In the accompanying drawings of the embodiments of the present invention, the same or similar reference numerals correspond to the same or similar components. In the description of the present invention, it should be understood that if terms such as "upper," "lower," "left," "right," "inner," and "outer" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, they are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the terms used to describe positional relationships in the drawings are only for illustrative purposes and should not be construed as limiting the present patent. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

[0020] In the description of this invention, unless otherwise explicitly specified and limited, the term "connection" or similar designation indicating a connection between components should be interpreted broadly. For example, it can refer to a fixed connection, a detachable connection, or an integral part; 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 refer to the internal communication between two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0021] A gear pump with pressure-splitting section topology reconfiguration according to the present invention, such as Figure 1-9 As shown, it includes a pump body 2, a front pump cover 1, a rear pump cover 3, and a main shaft 4. The pump body 2 has a cycloidal pump chamber 21, a gear pump chamber 22, and a main shaft hole 23 located at the front. The cycloidal pump chamber 21 has an inlet 201 that connects to the outside, and the gear pump chamber 22 has an outlet 202 that connects to the outside. A U-shaped inner flow channel 203 connecting the cycloidal pump chamber 21 and the gear pump chamber 22 is also provided in the pump body 2. That is, the cycloidal pump chamber 21 is connected to the inner flow channel inlet 2031, and the gear pump chamber 22 is connected to the inner flow channel outlet 2032. A cycloidal pump assembly 5 is provided in the cycloidal pump chamber 21, and a gear pump assembly 6 is provided in the gear pump chamber 22. An overflow channel 71 is also provided inside the pump body 2. The overflow channel 71 connects the U-shaped inner channel 203 and the inlet 201. An overflow valve 7 is provided on the overflow channel 71.

[0022] The cycloidal pump assembly 5 includes an inlet distribution plate 51, an outer rotor 52, an inner rotor 53, and an outlet distribution plate 54. The outer rotor 52 meshes with the inner rotor 53, and the inner rotor 53 is connected to the main shaft 4.

[0023] like Figure 10-12 As shown, the inlet distribution plate 51 has an arc-shaped through groove 511, the width of which gradually decreases. The inlet distribution plate 51 also has a side oil port 512 that connects the widest part of the arc-shaped through groove 511 to the inlet 201.

[0024] A distribution plate positioning pin hole 14 is provided on the inner end face 11 of the front pump cover 1, and a positioning pin 513 is provided on the inlet distribution plate 51. The inlet distribution plate 51 is connected to the distribution plate positioning pin hole 14 on the inner end face 11 of the front pump cover 1 through the positioning pin 513. A pump body positioning pin hole 13 adapted to the positioning pin on the pump body 2 is also provided on the inner end face 11, the purpose of which is to achieve circumferential positioning and prevent rotation.

[0025] The outlet distribution plate 54 has an arc-shaped through groove 541, which gradually widens. A side oil port 542 is also provided on the outlet distribution plate 54, connecting the widest part of the arc-shaped through groove 541 to the inlet of the U-shaped inner flow channel 203. The structure of the outlet distribution plate 54 is the same as that of the inlet distribution plate 51, but its orientation is reversed.

[0026] An outlet distribution plate positioning pin hole is provided on the bottom surface of the cycloidal pump chamber 21, and another positioning pin is provided on the outlet distribution plate 54. The outlet distribution plate 54 is connected to the outlet distribution plate positioning pin hole on the bottom surface of the cycloidal pump chamber 21 through the other positioning pin. This achieves circumferential positioning and prevents rotation.

[0027] Given that sealing groove 15, sealing groove 2, and sealing groove 3633 are all conventional structures, they will not be described in detail in this case.

[0028] Furthermore, the rear pump cover 3 has an 8-shaped cavity 31, and an 8-shaped sleeve 63 is provided inside the 8-shaped cavity 31. The 8-shaped sleeve 63 has an upper shaft hole 631 and a lower shaft hole 632. A bearing 64 is provided in the upper shaft hole 631, and a bearing 65 is provided in the lower shaft hole 632. The gear pump assembly 6 includes a driving gear 61 and a driven gear 62. The driving gear 61 is connected to the main shaft 4. The main shaft 4 is movably connected to the main shaft hole 23 in the middle and the tail end of the main shaft 4 is movably connected to the bearing 64. The driven gear 62 meshes with the driving gear 61. The driven gear 62 has a short shaft. One end of the short shaft passes through the driven shaft hole 24 and is movably connected to the pump body 2, and the other end is connected to the bearing 65.

[0029] Furthermore, the working displacement of the cycloidal pump assembly 5 is Vc, the working displacement of the gear pump assembly 6 is Vg, and the rotational speed of the main shaft 4 is n; therefore, the flow rate of the cycloidal pump assembly 5 is Qc = Vc × n, and the flow rate of the gear pump assembly 6 is Qg = Vg × n. Qc≥Qg×(1+δ) In the formula, δ is the comprehensive margin coefficient for manufacturing error, leakage and changes in medium viscosity.

[0030] Cycloidal pump assembly 5 and gear pump assembly 6 achieve synchronous rotational speed (i.e., the same n) by sharing a main shaft 4. Let the theoretical displacement of cycloidal pump assembly 5 be Vc and the theoretical displacement of gear pump assembly 6 be Vg, then the theoretical flow rates of the two stages are Qc = Vc × n and Qg = Vg × n, respectively. By optimizing the tooth difference, eccentricity, and tooth width of the cycloidal pump section, as well as the geometric parameters such as the tooth number difference, module, and tooth width of the external meshing section, the stages satisfy a series oil supply relationship, preferably satisfying Qc ≥ Qg × (1 + δ), thereby avoiding insufficient oil supply, cavitation, or pressure oscillation on the suction side of the external meshing section III.

[0031] To absorb transient pulsations and minor flow mismatches, an interstage transition zone II is set between the outlet of the inner meshing section I and the suction chamber of the outer meshing section III, and is connected to the first-stage suction chamber through a damping orifice and an overflow valve structure. When the pressure in the interstage transition zone II exceeds a set threshold, a portion of the oil is returned to the suction chamber of the inner meshing section, achieving interstage flow-pressure self-balancing without the need for external control devices.

[0032] Pressure gradient distribution: the inner meshing section I undertakes the primary pressurization of 0-15MPa, the outer meshing section III completes the final pressurization of 15-30MPa, and the interstage transition zone II achieves smooth connection through flow channel optimization.

[0033] Combination Figure 13-15 Explanation of the working principle of this invention: (1) Oil suction stage (low pressure zone): Cycloidal pump assembly 5 starts: the main shaft 4 drives the inner rotor 53 to rotate, forming a continuously changing sealed cavity with the outer rotor 52.

[0034] Volume expansion for oil suction: The volume of the oil suction side sealing cavity gradually increases, forming a negative pressure, and the oil is sucked into the cavity from the inlet 201.

[0035] Smooth flow output: The continuous engagement characteristic of the cycloidal pump assembly 5 ensures stable flow output (pulsation rate < ±5%).

[0036] Enhanced self-priming capability: The effective oil suction volume of the cycloidal pump assembly 5 (30% higher than that of the gear pump assembly 6) significantly reduces the risk of cavitation.

[0037] Low-pressure leakage suppression: The cycloidal gear has excellent gap sealing effect under low pressure.

[0038] (2) Primary boosting stage (transition from internal meshing section to external meshing section): Oil transfer: The oil output from the internal meshing section I enters the suction side chamber of the external meshing section III through the distribution plate. An interstage transition zone II is set between the outlet of the internal meshing section I and the inlet of the external meshing section III, and an intermediate buffer chamber is set in the interstage transition zone II. The intermediate buffer chamber serves as the core volume unit of the pressure-sharing section.

[0039] Damping and pressure stabilization: Throttling structures are set at the inlet and outlet of the intermediate buffer chamber or in the interstage flow channel connected to it to provide damping for interstage pressure fluctuations, making pressure changes smoother; at the same time, the volume of the buffer chamber is used to absorb the transient pulsation of the first stage output and the pressure oscillation caused by the slight mismatch of the two stages, thereby improving the stability of the two-stage series fuel supply.

[0040] The overflow valve 7 is located in the valve chamber communicating with the damping orifice section, and the buffer chamber only serves as a "buffer volume". When the interstage pressure exceeds the set threshold, the overflow valve 7 opens, allowing some of the oil in the buffer chamber to flow back to the low-pressure side, achieving the following function: 1. Limit / stabilize the pressure between stages to form the pressure boundary of the "pressure distribution section"; Second, unload and release interstage pressure fluctuations to reduce interstage pressure oscillations and surges; Third, it absorbs transient energy during startup and sudden load changes, improves the inlet conditions of the external meshing section, and reduces the risk of cavitation. Fourth, when the primary supply flow rate instantaneously exceeds the secondary intake demand, a return channel for the excess flow rate is provided to achieve interstage flow-pressure self-balancing.

[0041] (3) Final pressurization stage (high pressure zone): Cycloidal pump assembly 5 engages and pressurizes: the driving gear 61 and the driven gear 62 mesh, the volume of the oil discharge side sealing cavity gradually decreases, and the oil is squeezed out from the outlet 202.

[0042] Gap compensation sealing and radial force balance: A floating side plate is set in the high pressure zone. The floating side plate achieves adaptive compensation of the end face gap under the action of high pressure oil. At the same time, a balance oil passage connected to the oil discharge side is formed on the floating side plate, so that the high pressure action area tends to be symmetrical in the radial direction, thereby weakening the unbalanced hydraulic radial force and reducing the gear shaft eccentric torque and bearing load.

[0043] This invention utilizes the meshing principle of the gear pump assembly 6 and the cycloidal pump assembly 5 to ensure that the center of the inner rotor 53 of the cycloidal pump assembly 5 is coaxial with the driving gear 61 of the gear pump assembly 6, and performs gear parameter matching. The tooth number difference between the outer rotor 52 and the inner rotor 53 is 1 (e.g., 6:7), while the driving gear 61 and the driven gear 62 use a standard tooth number ratio of 12:12. Module matching: The module of the inner meshing section I is smaller (e.g., 1.5mm), and the module of the outer meshing section III is larger (e.g., 3mm) to adapt to the loads of different pressure sections. Speed ​​synchronization: The inner and outer gear pairs achieve consistent speed through coaxial drive, avoiding flow mismatch between stages.

[0044] The inlet is set by adjusting the eccentric position of the cycloidal rotor. The low-pressure input pump outer rotor 52 is installed on the left side of the main shaft, and the high-pressure booster pump gear is installed on the right side of the main shaft 4. The outlet of the low-pressure input pump can be directly connected to the high-pressure booster pump. That is, the hydraulic medium flows from the cycloidal pump inlet M1 to the cycloidal pump outlet M2, then through the interstage transition zone II to the inlet N1 of the external gear pump, and finally flows to the outlet N2 of the external gear pump, realizing two-stage oil supply. According to the inherent meshing characteristics of gears, the fluid is transported by the relative motion between the gears (one internal gear and one external gear). The size of the meshing cavity changes periodically, which solves the flow pulsation caused by the change of pump cavity volume and provides a stable flow rate for the outlet of the high-pressure booster pump.

[0045] The pump is designed for a speed of 8000 r / min. The inlet suction cycloidal pump has 6 / 7 teeth on both the inner and outer rotors, an eccentricity e = 2 mm, a creation factor k = 1.2, an arc radius factor h = 0.38, a rotor tooth width B = 15 mm, a maximum volumetric cavity area Amax = 119.625 mm², and a minimum volumetric cavity area Amin = 3.196 mm². The pump flow rate can be calculated as Q = ωZB(Amax - Amin) = 83.8 L / min. The outlet is a 12-tooth external gear pump with a module of 2.5mm, a minimum displacement coefficient of 0.3, and a rotor tooth width of 18mm. The calculated actual flow rate of the external gear pump is 72L / min. The output flow rate of the upper-stage cycloidal pump is 1.16 times that of the lower-stage external gear pump. By fully utilizing the "self-priming" advantage of the cycloidal pump and combining it with the high output pressure of the external gear pump, a gear pump with synergistic optimization of high self-priming efficiency in the low-pressure zone and low leakage in the high-pressure zone is achieved.

[0046] It should be stated that the above-described specific embodiments are merely preferred embodiments of the present invention and the technical principles employed. Those skilled in the art should understand that various modifications, equivalent substitutions, and variations can be made to the present invention based on the technical content disclosed in this application. However, such variations, as long as they do not depart from the spirit of the present invention, should be within the protection scope of the present invention. Furthermore, some terminology used in this specification and claims is not limiting but merely for ease of description.

Claims

1. A gear pump with topological reconfiguration of pressure-dividing section, comprising a pump body (2), a front pump cover (1), a rear pump cover (3), and a main shaft (4), characterized in that, The pump body (2) has a cycloidal pump chamber (21), a gear pump chamber (22) and a main shaft hole (23) located at the front. The cycloidal pump chamber (21) has an inlet (201) that connects to the outside, and the gear pump chamber (22) has an outlet (202) that connects to the outside. The pump body (2) also has a U-shaped inner flow channel (203) that connects the cycloidal pump chamber (21) and the gear pump chamber (22). A cycloidal pump assembly (5) is provided in the cycloidal pump chamber (21), and a gear pump assembly (6) is provided in the gear pump chamber (22). An overflow channel (71) is also provided inside the pump body (2). The overflow channel (71) connects the U-shaped inner channel (203) and the inlet (21). An overflow valve (7) is provided on the overflow channel (71).

2. The gear pump with topology reconfiguration of the pressure-sharing section according to claim 1, characterized in that, The cycloidal pump assembly (5) includes an inlet distribution plate (51), an outer rotor (52), an inner rotor (53) and an outlet distribution plate (54). The outer rotor (52) meshes with the inner rotor (53), and the inner rotor (53) is connected to the main shaft (4).

3. The gear pump with topology reconfiguration of the pressure-sharing section according to claim 2, characterized in that, The inlet distribution plate (51) is provided with an arc-shaped through groove (511), the width of which gradually decreases. A side oil port (512) is also provided on the inlet distribution plate (51) to connect the widest part of the arc-shaped through groove (511) to the inlet (201).

4. The gear pump with pressure-sharing section topology reconfiguration according to claim 3, characterized in that, A distribution plate positioning pin hole (14) is provided on the inner end face (11) of the front pump cover (1), and a positioning pin (513) is provided on the inlet distribution plate (51). The inlet distribution plate (51) is connected to the distribution plate positioning pin hole (14) on the inner end face (11) of the front pump cover (1) through the positioning pin (513).

5. A gear pump with topology reconfiguration of the pressure-sharing section according to claim 2, characterized in that, The outlet distribution plate (54) is provided with an arc-shaped through groove two (541), the width of the arc-shaped through groove two (541) gradually widens, and a side oil port two (542) is also provided on the outlet distribution plate (54) to connect the widest part of the arc-shaped through groove two (541) to the inlet of the U-shaped inner flow channel (203).

6. A gear pump with topology reconfiguration of the pressure-sharing section according to claim 5, characterized in that, An outlet distribution plate positioning pin hole is provided on the bottom surface of the cycloidal pump chamber (21), and another positioning pin is provided on the outlet distribution plate (54). The outlet distribution plate (52) is connected to the outlet distribution plate positioning pin hole on the bottom surface of the cycloidal pump chamber (21) through the other positioning pin.

7. A gear pump with topology reconfiguration of the pressure-sharing section according to claim 1, characterized in that, The rear pump cover (3) has a rear pump cover figure-eight shaped cavity (31), and an 8-shaped sleeve (63) is provided in the rear pump cover figure-eight shaped cavity (31). The figure-eight shaped sleeve (63) has an upper shaft hole (631) and a lower shaft hole (632). A bearing one (64) is provided in the upper shaft hole (631), and a bearing two (65) is provided in the lower shaft hole (632). The gear pump assembly (6) includes a drive gear (61) and a driven gear (62). The drive gear (61) is connected to the main shaft (4). The main shaft (4) is movably connected to the main shaft hole (23) in the middle and the bearing (64) is movably connected to the tail end of the main shaft (4). The driven gear (62) meshes with the drive gear (61). The driven gear (62) has a short shaft. One end of the short shaft is movably connected to the pump body (2) and the other end is connected to the bearing (65).

8. A gear pump with topology reconfiguration of the pressure-sharing section according to claim 1, characterized in that, The working displacement of the cycloidal pump assembly (5) is Vc, the working displacement of the gear pump assembly (6) is Vg, and the rotational speed of the main shaft (4) is n; then the flow rate of the cycloidal pump assembly (5) is Qc = Vc × n, and the flow rate of the gear pump assembly (6) is Qg = Vg × n. Qc≥Qg×(1+δ) In the formula, δ is the comprehensive margin coefficient for manufacturing error, leakage and changes in medium viscosity.

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