A low-wear rotary refrigerant pump

Abstract

The present invention discloses a low-wear rotary refrigerant pump, which comprises a housing, on which an inlet pipe for fluid input is provided; an end cover, which is fixed to the housing, and an liquid outlet groove for fluid output is provided on the end cover. On the side of the end cover close to the housing, a pump body is connected. The pump body is fixedly connected with a double-support pump cover, and a liquid inlet groove for fluid to enter the inside of the pump body is provided on the double-support pump cover. A thrust component is provided on the double-support pump cover; a rotor shaft, which penetrates through the end cover and is connected with a rotor assembly, and the rotor shaft is connected with the thrust component; by driving the rotor assembly to rotate through the rotor shaft, fluid is input into the housing from the inlet pipe, sucked into the pump body through the liquid inlet groove, and then discharged from the liquid outlet groove, so as to realize continuous liquid suction and liquid discharge of the fluid. The present invention can not only restrict the axial direction of the rotor shaft, reduce the sway of the rotor shaft along the axis direction, but also reduce the friction and wear when the rotor assembly meshes, improve the working efficiency of the refrigerant pump, and at the same time extend the service life of the refrigerant pump.

Description

Technical Field

[0001] The present invention relates to a low-wear rotary refrigerant pump. Background Art

[0002] Most existing heat pipe systems use ordinary liquid pumps to transport liquid refrigerant. Of course, there are even cases where a liquid pump is used and the liquid refrigerant is directly circulated by taking advantage of the height difference. However, without using a liquid pump, the flow effect of the refrigerant is poor, affecting the heat exchange efficiency of the system. Using an ordinary liquid pump has a high cost, low efficiency, and poor sealing effect. Therefore, in the refrigeration field, a refrigerant driving device has emerged for pressurizing the refrigerant in a liquid state. A refrigerant pump is one type of refrigerant driving device.

[0003] The refrigerant pump in the prior art cannot effectively constrain the axial direction of the rotor shaft. Therefore, the rotor shaft is prone to wobbling during continuous operation, and at the same time, the rotor mounted on the rotor shaft is also subject to frictional wear, reducing the service life of the refrigerant pump. Summary of the Invention

[0004] The purpose of the present invention is to provide a technical solution for a low-wear rotary refrigerant pump in view of the deficiencies of the prior art. It can not only constrain the axial direction of the rotor shaft, reduce the wobbling of the rotor shaft along the axis direction, but also reduce the frictional wear when the rotor components mesh, improve the working efficiency of the refrigerant pump, and at the same time extend the service life of the refrigerant pump.

[0005] To solve the above technical problems, the present invention adopts the following technical solutions:

[0006] A low-wear rotary refrigerant pump, characterized in that it includes

[0007] A housing, on which an inlet pipe for fluid input is provided;

[0008] An end cover fixed to the housing. An outlet groove for fluid output is provided on the end cover. A pump body is connected to the side of the end cover close to the housing. The pump body is fixedly connected with a double-support pump cover. An inlet groove for fluid to enter the interior of the pump body is provided on the double-support pump cover, and a thrust component is provided on the double-support pump cover;

[0009] A rotor shaft passing through the end cover and connecting a rotor assembly. The rotor assembly is located inside the pump body, and the rotor shaft is connected to the thrust component;

[0010] The rotor shaft drives the rotor assembly to rotate, so that the fluid is input into the housing from the inlet pipe, sucked into the pump body through the inlet groove, and then discharged from the outlet groove, realizing continuous liquid suction and liquid discharge of the fluid. Through the design of the above structure, not only can the axial direction of the rotor shaft be constrained, reducing the wobbling of the rotor shaft along the axis direction, but also the frictional wear when the rotor components mesh can be reduced, improving the working efficiency of the refrigerant pump, and at the same time extending the service life of the refrigerant pump.

[0011] Furthermore, the rotor assembly includes an outer rotor, an inner rotor and a pin shaft. The outer rotor is located in the second cavity of the pump body. The inner rotor is fixed on the rotor shaft and located in the first cavity of the outer rotor. The pin shaft is embedded between the inner rotating shaft and the outer rotor. The outer rotor and the inner rotor are eccentric. The inner rotor drives the outer rotor to rotate through the pin shaft, so that a continuously changing space is formed between the inner rotor and the outer rotor, realizing the continuous suction and discharge of the fluid. Through the design of the pin shaft, the friction and wear between the outer rotor and the inner rotor during rotation can be greatly reduced, which is convenient for replacement. At the same time, the manufacturing and maintenance costs are reduced. At the same time, due to the eccentric setting of the inner rotor and the outer rotor, the space between the inner rotor and the outer rotor can be increased from small to large to realize liquid suction, and decreased from large to small to realize liquid discharge, and this process is continuously carried out in a cycle.

[0012] Furthermore, the pin shaft meshes with the outer rotor to form a rotor profile. The rotor profile is formed by connecting several arcs end to end. Each arc consists of an arc segment FG and an arc segment GH. Both the arc segment FG and the arc segment GH convex towards the center of the rotor profile, and the arc segment FG is tangent to the arc segment GH.

[0013] Furthermore, the equation of the arc segment FG is , where R1 is the pitch circle radius of the inner rotor, r1 is the outer circumferential radius of the pin shaft, and 120 < t1 < 360.

[0014] Furthermore, the equation of the arc segment GH is , where R1 is the pitch circle radius of the inner rotor, r1 is the outer circumferential radius of the pin shaft, z1 is the number of teeth of the outer rotor, z2 is the number of teeth of the inner rotor, and 240 - t1 < t2 < 300 - t1.

[0015] Furthermore, the thrust assembly includes a thrust gland, a first bearing, a second bearing and a base. The thrust gland is fixed on the double-support pump cover. The first bearing is sleeved on the rotor shaft. The base is connected to the inner rotor. One end of the first bearing abuts against the thrust gland, and the other end of the first bearing abuts against the base through the second bearing. Through the design of the thrust gland, the first bearing, the second bearing and the base, the axial positioning of the rotor assembly can be carried out, and at the same time, the connection stability between the rotor assembly and the rotor shaft is improved. The first bearing can limit the radial direction of the rotor shaft and reduce the shaking of the rotor shaft.

[0016] Furthermore, the first bearing is a sliding bearing. The first bearing is provided with a first through hole, a first oil guide groove and a second oil guide groove. The first oil guide groove is distributed in the first through hole, and the first oil guide groove communicates with the second oil guide groove. Through the first oil guide groove and the second oil guide groove, the flow of lubricating oil is facilitated, and the friction and wear are reduced.

[0017] Further, the second bearing is a thrust bearing, and the second bearing is embedded in the first card slot of the base. The base is connected to the inner rotor through a fastener, and the base can rotate together with the inner rotor.

[0018] Further, the liquid outlet groove and the liquid inlet groove are arranged vertically staggered, so that the fluid is sucked into the pump body from the lower liquid inlet groove and discharged from the upper liquid outlet groove, facilitating the stable flow of the fluid.

[0019] Further, the rotor shaft is connected to the end cover through a third bearing, and the third bearing can limit the radial direction of the rotor shaft to reduce the sway of the rotor shaft.

[0020] Due to the adoption of the above technical solutions, the present invention has the following beneficial effects:

[0021] 1. The present invention can not only constrain the axial direction of the rotor shaft, reduce the sway of the rotor shaft along the axis direction, but also reduce the friction and wear during the meshing of the rotor assembly, improve the working efficiency of the refrigerant pump, and extend the service life of the refrigerant pump at the same time.

[0022] 2. Through the design of the pin shaft, the friction and wear between the outer rotor and the inner rotor during rotation can be greatly reduced, which is convenient for replacement, and at the same time, the manufacturing and maintenance costs are reduced. At the same time, due to the eccentric setting of the inner rotor and the outer rotor, the space between the inner rotor and the outer rotor can change from small to large to achieve liquid suction, and from large to small to achieve liquid discharge, and this process is continuously repeated.

[0023] 3. Through the design of the thrust gland, the first bearing, the second bearing and the base, the axial positioning of the rotor assembly can be realized, and at the same time, the connection stability between the rotor assembly and the rotor shaft is improved. The first bearing can limit the radial direction of the rotor shaft to reduce the sway of the rotor shaft. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The present invention will be further described below with reference to the drawings:

[0025] Figure 1 is the effect diagram of a low-wear rotor type refrigerant pump of the present invention;

[0026] Figure 2 is the exploded view of the present invention;

[0027] Figure 3 is Figure 1 the front view of;

[0028] Figure 4 is Figure 3 the cross-sectional schematic view in the A-A direction of;

[0029] Figure 5 is the effect diagram of the housing in the present invention;

[0030] Figure 6 This is the effect diagram of the double - supported pump cover in the present invention;

[0031] Figure 7 It is Figure 6 the schematic structural diagram in the B direction in;

[0032] Figure 8 This is the effect diagram of the base in the present invention;

[0033] Figure 9 This is the effect diagram of the first bearing in the present invention;

[0034] Figure 10 It is Figure 9 the effect diagram in the C direction in;

[0035] Figure 11 This is the effect diagram of the inner rotor in the present invention;

[0036] Figure 12 This is the effect diagram of the outer rotor in the present invention;

[0037] Figure 13 This is the effect diagram of the pump body in the present invention;

[0038] Figure 14 This is the effect diagram of the end - cover in the present invention;

[0039] Figure 15 It is Figure 14 the schematic structural diagram in the D direction in;

[0040] Figure 16 This is the effect diagram of the rotor shaft in the present invention;

[0041] Figure 17 This is the connection schematic diagram among the inner rotor, outer rotor, pin shaft and pump body in the present invention.

[0042] Figure 18 This is the rolling schematic diagram of the inner rotor, pin shaft and outer rotor in the present invention;

[0043] Figure 19 This is the schematic structural diagram of the rotor profile in the present invention;

[0044] Figure 20 This is the schematic structural diagram of the arc shapes of the outer rotor and inner rotor with three different R1 values in the present invention.

[0045] In the figure: 1 - housing; 101 - inlet pipe;

[0046] 2 - rotor shaft; 201 - first keyway; 202 - first shaft section; 203 - second shaft section;

[0047] 3 - end - cover; 301 - first threaded hole; 302 - first shaft hole; 303 - first arc - shaped groove; 304 - liquid outlet groove;

[0048] 4 - Double - support pump cover; 401 - Mounting hole; 402 - Support sleeve; 403 - Second threaded hole; 404 - Liquid inlet groove; 405 - Second arc - shaped groove;

[0049] 5 - Base; 501 - First card slot; 502 - Base pin;

[0050] 6 - First bearing; 601 - First through - hole; 602 - First U - shaped groove; 603 - First oil - guiding groove; 604 - Second oil - guiding groove;

[0051] 7 - Inner rotor; 701 - Second keyway; 702 - Arc - shaped surface; 703 - Limiting groove; 704 - Positioning hole; 705 - Second card slot;

[0052] 8 - Outer rotor; 801 - First cavity; 802 - First arc segment; 803 - Second arc segment;

[0053] 9 - Pump body; 901 - Second cavity; 902 - Second through - hole; 903 - Sealing groove;

[0054] 10 - Thrust gland; 11 - First screw; 12 - Second bearing; 13 - Fixed key; 14 - Pin shaft; 15 - Second screw; 16 - Cylindrical pin; 17 - Snap ring; 18 - O - ring; 19 - Third bearing. Detailed implementation manners

[0055] It should be noted that, without conflict, the embodiments and features in the embodiments of the present application may be combined with each other. The present invention will be described in detail below with reference to the drawings and in combination with the embodiments.

[0056] In order to enable those skilled in the art to better understand the solution of the present invention, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0057] It should be noted that the terms "first", "second", etc. in the description and claims of the present invention and the above - mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. In addition, the terms "comprising" and "having" and any variations thereof are intended to cover non - exclusive inclusion.

[0058] Such as Figures 1 to 5As shown in the figure, a low-wear rotary refrigerant pump of the present invention includes a housing 1, an end cover 3, and a rotor shaft 2. The housing 1 is welded and fixed to the end cover 3. A cavity is formed inside the housing 1. An inlet pipe 101 for fluid input is provided on the housing 1, and the inlet pipe 101 communicates with the cavity to facilitate the fluid to flow into the cavity. The fluid in this application mainly refers to the coolant.

[0059] As Figure 14 and Figure 15 shown in the figure, an liquid outlet groove 304 for fluid output is provided on the end cover 3. The liquid outlet groove 304 horizontally penetrates the end cover 3. A first shaft hole 302 is provided on the end cover 3, and the first shaft hole 302 matches the rotor shaft 2. The rotor shaft 2 is connected to the end cover 3 through a third bearing 19. The third bearing 19 can limit the radial direction of the rotor shaft 2 and reduce the sway of the rotor shaft 2. At the same time, a first arc-shaped groove 303 and a first threaded hole 301 are provided on one side of the end cover 3 close to the pump body 9. The first arc-shaped groove 303 does not penetrate the end cover 3 and is symmetrically distributed on both sides of the first shaft hole 302 with the liquid outlet groove 304. The first arc-shaped groove 303 can buffer the fluid. Four first threaded holes 301 are distributed on the shown end cover 3.

[0060] One side of the end cover 3 close to the housing 1 is connected to the pump body 9. As Figure 13 shown in the figure, sealing grooves 903 are provided on both end faces of the pump body 9. O-rings 18 are embedded in the sealing grooves 903, which improves the sealing effect between the pump body 9 and the end cover 3 and the double-support pump cover 4. Four second through holes 902 corresponding to the first threaded holes 301 one by one are provided on the pump body 9. The second through holes 902 penetrate the pump body 9.

[0061] The pump body 9 is fixedly connected to a double-support pump cover 4. As Figure 6 and Figure 7 shown in the figure, a liquid inlet groove 404 for fluid to enter the inside of the pump body 9 is provided on the double-support pump cover 4. The liquid inlet groove 404 penetrates the double-support pump cover 4. A support sleeve 402 is provided on one side of the double-support pump cover 4 far from the end cover 3. A second shaft hole is provided on the support sleeve 402, and the second shaft hole matches the rotor shaft 2. Second threaded holes 403 are annularly distributed on the end face of the support sleeve 402. A second arc-shaped groove 405 is provided on one side of the double-support pump cover 4 close to the pump body 9. The second arc-shaped groove 405 and the liquid inlet groove 404 are symmetrically distributed on both sides of the second shaft hole. The second arc-shaped groove 405 can buffer the fluid. Four mounting holes 401 corresponding to the second through holes 902 one by one are provided on the double-support pump cover 4. By sequentially passing second screws 15 through the mounting holes 401, the second through holes 902, and the first threaded holes 301, the fixed assembly between the double-support pump cover 4, the pump body 9, and the end cover 3 can be realized, and the installation and disassembly are convenient and fast.

[0062] The double-support pump cover 4 is provided with a thrust component, and the rotor shaft 2 is connected to the thrust component. The thrust component includes a thrust gland 10, a first bearing 6, a second bearing 12, and a base 5. The thrust gland 10 is fixed in the second threaded hole 403 on the double-support pump cover 4 through a first screw 11. The first bearing 6 is sleeved on the second shaft section 203 of the rotor shaft 2. The base 5 is connected to the inner rotor 7, and the base 5 is a stainless-steel base 5.

[0063] One end of the first bearing 6 abuts against the thrust gland 10, and the other end of the first bearing 6 abuts against the base 5 through the second bearing 12. Through the design of the thrust gland 10, the first bearing 6, the second bearing 12, and the base 5, the axial positioning of the rotor assembly can be carried out, and at the same time, the connection stability between the rotor assembly and the rotor shaft 2 is improved. The first bearing 6 can limit the radial direction of the rotor shaft 2 and reduce the sway of the rotor shaft 2.

[0064] As Figure 9 and Figure 10 shown, the first bearing 6 is a sliding bearing. The first bearing 6 is provided with a first through hole 601, a first oil guide groove 603, and a second oil guide groove 604. The first oil guide groove 603 is distributed in the first through hole 601, and the second oil guide groove 604 is distributed on the end face close to the second bearing 12. The first oil guide groove 603 and the second oil guide groove 604 are communicated with each other. Through the first oil guide groove 603 and the second oil guide groove 604, the flow of lubricating oil is facilitated, and the friction and wear are reduced. At the same time, a first U-shaped groove 602 is provided on one side of the first bearing 6 close to the double-support pump cover 4, and a second U-shaped groove is provided on the double-support pump cover 4. The first U-shaped groove 602 and the second U-shaped groove are positioned through a cylindrical pin 16. The cylindrical pin 16 fits on the inner wall of the support sleeve 402 to prevent the sliding bearing from rotating during the rotation of the inner rotor 7 driving the base 5, and the installation stability of the rotor shaft 2 is improved.

[0065] The second bearing 12 is a thrust bearing. The second bearing 12 is embedded in the first clamping groove 501 of the base 5. As Figure 8 shown, the base 5 is connected to the inner rotor 7 through a fastener. The fastener is a base pin 502. A positioning hole 704 is provided on the inner rotor 7. The positioning hole 704 matches the base pin 502, so that the base 5 can rotate together with the inner rotor 7. The material of the second bearing 12 is silicon carbide ceramic.

[0066] As Figure 11 and Figure 12As shown, the rotor shaft 2 penetrates through the end cover 3 and is connected to the rotor assembly, and the rotor assembly is located inside the pump body 9. The rotor assembly includes an outer rotor 8, an inner rotor 7, and a pin shaft 14. The outer rotor 8 is located inside the second cavity 901 of the pump body 9. The inner rotor 7 is fixed to the rotor shaft 2 and is located inside the first cavity 801 of the outer rotor 8. The pin shaft 14 is embedded between the inner rotating shaft and the outer rotor 8. The outer rotor 8 and the inner rotor 7 are eccentric. The inner rotor 7 drives the outer rotor 8 to rotate through the pin shaft 14, so that a continuously changing space is formed between the inner rotor 7 and the outer rotor 8, realizing the continuous suction and discharge of fluid. Through the design of the pin shaft 14, the friction and wear between the outer rotor 8 and the inner rotor 7 during rotation can be greatly reduced, which is convenient for replacement, and at the same time, the manufacturing and maintenance costs are reduced. At the same time, since the inner rotor 7 and the outer rotor 8 are eccentrically arranged, the space between the inner rotor 7 and the outer rotor 8 can realize liquid suction from small to large and liquid discharge from large to small, and this process is continuously carried out in a cycle. The rotor assembly is driven to rotate by the rotor shaft 2, so that the fluid is input into the housing 1 from the inlet pipe 101, sucked into the pump body 9 through the liquid inlet groove 404, and then discharged from the liquid outlet groove 304, realizing the continuous suction and discharge of fluid; the liquid outlet groove 304 and the liquid inlet groove 404 are arranged vertically staggered to enable the fluid to be sucked into the pump body 9 from the lower liquid inlet groove 404 and discharged from the upper liquid outlet groove 304, facilitating the stable flow of the fluid.

[0067] Both ends of the inner rotor 7 are provided with second clamping grooves 705, and the second clamping grooves 705 are matched with the base 5. An elastic retaining ring 17 is provided between the inner rotor 7 and the end cover 3, and the elastic retaining ring 17 is limited in the second clamping groove 705. The design of the elastic retaining ring 17 can generate an axial thrust on the inner rotor 7, so as to ensure the connection stability between the inner rotor 7 and the thrust component.

[0068] Arc surfaces 702 and limiting grooves 703 are arranged at intervals on the outer side surface of the inner rotor 7. The radius of the arc surface 702 is greater than the radius of the limiting groove 703. The limiting groove 703 is matched with the pin shaft 14. The inner side surface of the outer rotor 8 is formed by the head-to-tail connection of a first arc segment 802 and a second arc segment 803. The radius of the first arc segment 802 is greater than the radius of the second arc segment 803.

[0069] As Figures 18 to 20 shown, both the inner rotor and the outer rotor are centrosymmetric about their own rotor shaft centers Oa and Ob. The inner rotor drives the outer rotor to rotate through the pin shaft. The pin shaft and the outer rotor rotate to form a rotor profile. The rotor profile is obtained by calculation. The rotor profile is formed by the head-to-tail connection of six arc segments and is an axisymmetric closed structure. The pin shaft meshes with the outer rotor to form a rotor profile. The rotor profile is formed by the head-to-tail connection of several arc segments. In this application, six arc segments are taken as an example. Each arc segment is composed of an arc segment FG and an arc segment GH. Both the arc segment FG and the arc segment GH convex towards the center of the rotor profile. The arc segment FG is tangent to the arc segment GH. The arc segment GH does not mesh with the outer rotor during rotation.

[0070] This application takes R1 = 32; r1 = 4; e = 4; z1 = 7; z2 = 6; r3 = e * z2 as an example.

[0071] The angle by which the inner rotor rotates around the center Oa is o1, and the range of o1 is 0 to 2π, where t1 = atan((sin(z1 * o1)) / ((R1 / r3) - cos(z1 * o1))), and 120 < t1 < 360.

[0072] The equation of the arc segment FG is , where R1 is the pitch circle radius of the inner rotor and r1 is the outer circumferential radius of the pin shaft.

[0073] The equation of the outer rotor is obtained through coordinate transformation of the FG segment of the inner rotor equation.

[0074] ;

[0075] Substitute the equation of the FG segment to get

[0076]

[0077] 6 * o1 = 7 * o2.

[0078] The arc segment GH and the arc segment tangent to it, such as Figure 6 The equation of the GH segment shown is as follows

[0079] ;

[0080] When t1 reaches 60 degrees, the equation of the arc segment GH is

[0081] ;

[0082] 180 < t2 < 240.

[0083] As Figure 17 shown, when the inner rotor 7 drives the pin shaft 14 to move, the arc surface 702 on the inner rotor 7 does not come into contact with the first arc segment 802 and the second arc segment 803 on the outer rotor 8. Only the outer circumferential side surface of the pin shaft 14 comes into contact with the first arc segment 802 and the second arc segment 803. When the pin shaft 14 moves along the first arc segment 802, the pin shaft 14 is in line contact with the first arc segment 802. When the pin shaft 14 moves along the second arc segment 803, the pin shaft 14 is in surface contact with the second arc segment 803.

[0084] As Figure 16As shown in the figure, a first shaft section 202 is provided on the rotor shaft 2, a first keyway 201 is provided on the first shaft section 202, a second keyway 701 is provided on the inner rotor 7, and a fixing key 13 is installed between the first keyway 201 and the second keyway 701, so as to realize the fixed assembly between the inner rotor 7 and the rotor shaft 2.

[0085] Through the design of the above structure, not only can the axial direction of the rotor shaft 2 be restricted to reduce the sway of the rotor shaft 2 along the axis direction, but also the friction and wear during the meshing of the rotor assembly can be reduced, the working efficiency of the refrigerant pump is improved, and at the same time, the service life of the refrigerant pump is prolonged.

[0086] The working principle of the present invention is as follows:

[0087] First, connect the refrigerant pump with an external coolant device, start the rotor shaft 2, drive the inner rotor 7 and the outer rotor 8 to rotate through the rotor shaft 2, the coolant enters the housing 1 through the inlet pipe 101, and is sucked into the pump body 9 through the liquid inlet groove 404 on the double-support pump cover 4, and enters the smaller space between the inner rotor 7 and the outer rotor 8 to form liquid suction. As the rotor shaft 2 continues to rotate, this space continues to become larger until the maximum space is reached to complete the liquid suction. The rotor shaft 2 continues to rotate, and this space gradually becomes smaller from large, discharges the coolant in the space, and outputs it through the liquid outlet groove 304 on the end cover 3, realizing the continuous suction and discharge of the coolant.

[0088] The above are only specific embodiments of the present invention, but the technical features of the present invention are not limited thereto. Any simple changes, equivalent replacements or modifications made based on the present invention to achieve basically the same technical effects are all covered by the protection scope of the present invention.

Claims

1. A low-wear rotary refrigerant pump, characterized in that: including a housing, on which an inlet pipe for fluid input is provided; an end cover fixed to the housing, on which a liquid outlet groove for fluid output is provided. A pump body is connected to one side of the end cover close to the housing. The pump body is fixedly connected with a double-support pump cover, on which a liquid inlet groove for fluid to enter the pump body is provided, and a thrust component is provided on the double-support pump cover; a rotor shaft passing through the end cover and connecting a rotor assembly. The rotor assembly is located inside the pump body, and the rotor shaft is connected to the thrust component; the rotor assembly includes an outer rotor, an inner rotor and a pin shaft. The outer rotor is located in the second cavity of the pump body. The inner rotor is fixed to the rotor shaft and is located in the first cavity of the outer rotor. The pin shaft is embedded between the inner rotor and the outer rotor. The outer rotor and the inner rotor are eccentric, so that a continuously changing space is formed between the inner rotor and the outer rotor to realize continuous suction and discharge of the fluid; the thrust component includes a thrust gland, a first bearing, a second bearing and a base. The thrust gland is fixed to the double-support pump cover. The first bearing is sleeved on the rotor shaft. The base is connected to the inner rotor. One end of the first bearing abuts against the thrust gland, and the other end of the first bearing abuts against the base through the second bearing; the first bearing is a sliding bearing, and the first bearing is provided with a first through hole, a first oil guide groove and a second oil guide groove. The first oil guide groove is distributed in the first through hole, and the first oil guide groove communicates with the second oil guide groove; The rotor shaft drives the rotor assembly to rotate, so that the fluid is input into the housing from the inlet pipe, sucked into the pump body from the liquid inlet groove, and discharged from the liquid outlet groove, realizing continuous suction and discharge of the fluid.

2. The low-wear rotary refrigerant pump according to claim 1, characterized in that: The pin shaft meshes with the outer rotor to form a rotor profile, which is formed by connecting several arcs end to end. Each arc is composed of an arc segment FG and an arc segment GH. Both the arc segment FG and the arc segment GH convex towards the center of the rotor profile, and the arc segment FG is tangent to the arc segment GH.

3. The low-wear rotary refrigerant pump according to claim 1, characterized in that: The second bearing is a thrust bearing, which is embedded in the first card slot of the base, and the base is connected to the inner rotor through a fastener.

4. A low-wear rotary refrigerant pump according to claim 1, characterized in that: The liquid outlet groove and the liquid inlet groove are arranged vertically staggered, so that the fluid is sucked into the pump body from the lower liquid inlet groove and discharged from the upper liquid outlet groove.

5. The low-wear rotary refrigerant pump according to claim 1, characterized in that: The rotor shaft is connected to the end cover through a third bearing.

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