Pump body assembly, rotary cylinder pump and heat exchange equipment

Abstract

The utility model provides a pump body assembly, a rotary cylinder pump and heat exchange equipment, the pump body assembly comprises a rotating shaft, a cylinder sleeve, a piston sleeve and a piston, and the rotating shaft is provided with two eccentric parts along the axial direction of the rotating shaft; the rotating shaft and the cylinder sleeve are eccentrically arranged and the eccentric distance is fixed; the piston sleeve is rotatably arranged in the cylinder sleeve, two limiting channels of the piston sleeve are sequentially arranged in the axial direction of the rotating shaft, and the extending direction of the limiting channels is perpendicular to the axial direction of the rotating shaft; the two eccentric parts correspondingly extend into the two through holes of the two pistons, the two pistons are correspondingly and movably arranged in the two limiting channels and form a variable volume cavity, and the variable volume cavity is located in the moving direction of the pistons; and the projection of the piston in the axial direction of the through hole is circular. The piston of the fluorine pump solves the problems that the manufacturing cost of the fluorine pump is high and the economical efficiency of a rotary cylinder pump is not facilitated due to the fact that the piston of the fluorine pump in the prior art is complex to process.

Description

Technical Field

[0001] The utility model relates to the technical field of heat exchange systems, in particular to a pump body component, a rotary cylinder pump and a heat exchange device. Background Art

[0002] In data centers, computer room air conditioning and other fields, liquid pumps are usually used instead of compressors to drive the refrigerant to run in the air-conditioning system, and the energy efficiency is higher than that of conventional air-conditioning systems. The industry calls this system that uses a pump to drive the refrigerant a fluorine pump system, and the pump that drives the refrigerant is called a fluorine pump.

[0003] However, the processing of the piston of the existing fluorine pump is relatively complicated, resulting in a high manufacturing cost of the fluorine pump, which is not conducive to the economy of the rotary cylinder pump. Utility Model Content

[0004] The main purpose of the utility model is to provide a pump body assembly, a rotary cylinder pump and a heat exchange device to solve the problem that the processing of the piston of the fluorine pump in the prior art is relatively complicated, resulting in a high manufacturing cost of the fluorine pump and being unfavorable to the economy of the rotary cylinder pump.

[0005] In order to achieve the above-mentioned purpose, according to one aspect of the utility model, a pump body assembly is provided, including a rotating shaft, a cylinder sleeve, a piston sleeve and a piston, wherein the rotating shaft is provided with two eccentric parts along its axial direction; the rotating shaft and the cylinder sleeve are eccentrically arranged and the eccentric distance is fixed; the piston sleeve is rotatably arranged in the cylinder sleeve, and the piston sleeve has two limiting channels, the two limiting channels are arranged in sequence along the axial direction of the rotating shaft, and the extension direction of the limiting channels is perpendicular to the axial direction of the rotating shaft; the piston has a through hole, and there are two pistons, and the two eccentric parts extend into the two through holes of the two pistons respectively, and the two pistons are correspondingly movably arranged in the two limiting channels and form a variable volume chamber, and the variable volume chamber is located in the movable direction of the piston, and the rotating shaft rotates to drive the piston to move in the limiting channel while interacting with the piston sleeve, so that the piston sleeve and the piston rotate in the cylinder sleeve; wherein the axial projection of the piston in the through hole is circular.

[0006] Furthermore, the piston is cylindrical, and the extending direction of the through hole is consistent with the axial direction of the piston.

[0007] Furthermore, the outer diameter D of the piston hs The height H of the piston in its axial direction hs The ratio ranges from 0.5 to 2.

[0008] Furthermore, the inner diameter D of the piston hs2 The outer diameter D of the piston hs The ratio ranges from 0.2 to 0.8.

[0009] Furthermore, the piston has a rounded corner at the edge of the end surface facing the limiting channel, and the radius R of the rounded corner is smaller than the height H of the piston in the axial direction. hs , and the radius R of the fillet is smaller than the outer diameter D of the piston hs .

[0010] Furthermore, the minimum side thickness L1 of the limiting channel is equal to the outer diameter D of the piston sleeve. qw The ratio ranges from 0.05 to 0.3.

[0011] Furthermore, the height H of the connection between the two limiting channels in the axial direction of the piston sleeve is q2 The height H of the piston sleeve in its axial direction q1 The ratio ranges from 0.05 to 0.4.

[0012] Furthermore, the width W of the limiting channel q1 , Piston outer diameter D hs , Outer diameter of piston sleeve D qw Between: (W q1 -D hs ) / D qw The value range is 0 to 0.0025.

[0013] Furthermore, (W q1 -D hs ) / D qw The value range is 0.0002~0.0007.

[0014] Furthermore, a first chamfer R1 is provided at the edge of the end face of the piston facing the limiting channel, a second chamfer R2 is provided between the two channel side walls of the limiting channel and the channel bottom surface of the limiting channel, the first chamfer R1 is an annular chamfer opened at the edge of the end face of the piston facing the limiting channel, and the second chamfer R2 and the first chamfer R1 satisfy: R1≥R2.

[0015] Furthermore, the value range of the first chamfer R1 is 0.2-0.3 mm.

[0016] Furthermore, the second chamfer R2 and the first chamfer R1 satisfy: -0.1 mm<R2-R1<0 mm.

[0017] Furthermore, there is line contact between the outer peripheral surface of the piston and the channel wall of the limiting channel, so that the piston is rotatably arranged relative to the piston sleeve.

[0018] Furthermore, a third chamfer R3 is provided at the edge of the end face of the piston facing the limiting channel, and a fourth chamfer R4 is provided between the two channel side walls of the limiting channel and the channel bottom surface of the limiting channel. The third chamfer R3 is a partial chamfer opened at the edge of the end face of the piston facing the limiting channel, and the fourth chamfer R4 and the third chamfer R3 satisfy: R3≥R4.

[0019] Furthermore, the fourth chamfer R4 and the third chamfer R3 satisfy: -0.1 mm<R4-R3<0 mm.

[0020] Furthermore, the channel cross section of the limiting channel is adapted to the projection of the piston in the extension direction of the limiting channel, so that the piston is slidably disposed in the limiting channel.

[0021] Further, the first sealing distance Q1 between the piston and the piston sleeve is the minimum distance between the outer circle edge of the piston and the inner circle edge of the piston sleeve, wherein Q1>0.

[0022] Furthermore, the value range of the first sealing distance Q1 is 1 to 3 mm.

[0023] Furthermore, the first sealing distance Q1 and the outer diameter D of the piston hs , the inner diameter D1 of the piston sleeve satisfies: Q1=0.5×D hs -0.5×D1-2×e, where e is the eccentricity of the eccentric part.

[0024] Furthermore, a fifth chamfer R5 is provided at the edge of the end face of the piston facing the limiting channel, a sixth chamfer R6 is provided between the two channel side walls of the limiting channel and the channel bottom surface of the limiting channel, and the fifth chamfer R5 is an annular chamfer opened at the edge of the end face of the piston facing the limiting channel, and the sixth chamfer R6 and the fifth chamfer R5 satisfy: R5≥R6.

[0025] Furthermore, the value range of the fifth chamfer R5 is greater than 0.3 mm.

[0026] Furthermore, the sixth chamfer R6 and the fifth chamfer R5 satisfy: -0.1 mm<R6-R5<0 mm.

[0027] Furthermore, there is line contact between the outer peripheral surface of the piston and the channel wall of the limiting channel, so that the piston is rotatably arranged relative to the piston sleeve.

[0028] Furthermore, the second sealing distance Q2 between the piston and the piston sleeve is the minimum distance between the outer circle edge of the piston and the inner circle edge of the piston sleeve minus the fifth chamfer R5, wherein Q2>0.

[0029] Furthermore, the value range of the second sealing distance Q2 is 1 to 3 mm.

[0030] Furthermore, the second sealing distance Q2 and the piston outer diameter D hs , the inner diameter D1 of the piston sleeve and the fifth chamfer R5 satisfy: Q2 = 0.5 × D hs -0.5×D1-2×e-R5, where e is the eccentricity of the eccentric part.

[0031] Furthermore, there is a phase difference of a first angle A between the two eccentric portions, the eccentricities of the two eccentric portions are equal, and there is a phase difference of a second angle B between the extension directions of the two limiting channels, wherein the first angle A is twice the second angle B.

[0032] Furthermore, the two eccentric portions are arranged opposite to each other at an angle of 180°.

[0033] According to another aspect of the utility model, a rotary cylinder pump is provided, comprising a pump body assembly, and the pump body assembly is the above-mentioned pump body assembly.

[0034] According to another aspect of the utility model, a heat exchange device is provided, including a rotary cylinder pump, and the rotary cylinder pump is the rotary cylinder pump mentioned above.

[0035] By applying the technical solution of the utility model, the structural form of the piston is optimized so that the axial projection of the piston in the through hole is circular. This simplifies the processing technology of the piston and helps save the manufacturing cost of the pump body assembly, thereby ensuring the economy of the rotary cylinder pump. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] The drawings constituting part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation on the present invention. In the drawings:

[0037] Figure 1 A schematic diagram of the assembly structure of the piston sleeve and the piston of the pump body assembly according to the first embodiment of the utility model is shown;

[0038] Figure 2 Shows Figure 1 A schematic diagram of a structure in which the piston and the piston sleeve are in line contact;

[0039] Figure 3 Shows Figure 1 A schematic diagram of the structure of the piston sleeve;

[0040] Figure 4 Shows Figure 1 Schematic diagram of the structure of the piston;

[0041] Figure 5 A schematic diagram of the assembly structure of the piston sleeve and the piston of the pump body assembly according to the second embodiment of the utility model is shown;

[0042] Figure 6 Shows Figure 1 A schematic diagram of the structure of line contact and surface contact between the piston and the piston sleeve;

[0043] Figure 7 Shows Figure 5 A schematic diagram of the structure of the piston sleeve;

[0044] Figure 8 Shows Figure 5 Schematic diagram of the structure of the piston;

[0045] Fig. 9 Shows Figure 8 A schematic diagram of the structure of the piston from another perspective;

[0046] Fig.10 Shows Figure 8 A schematic diagram of the structure in the sliding direction of the piston;

[0047] Fig.11 A schematic diagram of the assembly structure of the piston sleeve and the piston of the pump body assembly according to the third embodiment of the present utility model is shown;

[0048] Fig.12 Shows Fig.11 A schematic diagram of the structure of the piston sleeve;

[0049] Fig.13 Shows Fig.11 Schematic diagram of the structure of the piston;

[0050] Fig.14 Shows Fig.11 A schematic diagram of the structure of the piston from another perspective;

[0051] Fig.15 A cross-sectional structural schematic diagram of a pump body assembly according to an optional embodiment of the utility model is shown;

[0052] Fig.16 Shows Fig.15 Schematic diagram of the enlarged structure at E in FIG.

[0053] Fig.17 Shows Fig.15 A schematic structural diagram of another embodiment at E in FIG.

[0054] Fig.18 Shows Figure 1 A schematic diagram of the structure of the piston from a top-down perspective;

[0055] Fig.19 Shows Fig.18 A schematic diagram of the structure of the piston in a side view;

[0056] Fig. 20 A schematic structural diagram of a crankshaft of a pump assembly according to an optional embodiment of the utility model is shown;

[0057] Fig.21 A schematic structural diagram of a piston sleeve of a pump body assembly according to an optional embodiment of the utility model is shown;

[0058] Fig. 22 Shows Fig.21 A schematic cross-sectional structure diagram of the piston sleeve at a ZZ perspective;

[0059] Fig.23 Shows Fig.21 A schematic structural diagram of the piston sleeve from a top view.

[0060] The above drawings include the following reference numerals:

[0061] 10. Rotating shaft; 11. Eccentric part;

[0062] 20. Cylinder liner;

[0063] 31. Piston sleeve; 311. Limiting channel; 312. Center hole; 32. Piston; 321. Through hole. DETAILED DESCRIPTION

[0064] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means a limitation on the utility model and its application or use. Based on the embodiments in the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0065] In order to solve the problem that the processing of the piston of the fluorine pump in the prior art is relatively complicated, resulting in high manufacturing costs of the fluorine pump and being unfavorable to the economy of the rotary cylinder pump, the utility model provides a pump body assembly, a rotary cylinder pump and a heat exchange device, wherein the rotary cylinder pump includes a pump body assembly, the pump body assembly is the above-mentioned and below-mentioned pump body assemblies, and the heat exchange device includes a rotary cylinder pump, and the rotary cylinder pump is the above-mentioned rotary cylinder pump.

[0066] Embodiment 1

[0067] like Figures 1 to 4As shown, the pump body assembly includes a rotating shaft 10, a cylinder sleeve 20, a piston sleeve 31 and a piston 32, wherein the rotating shaft 10 is provided with two eccentric parts 11 along its axial direction; the rotating shaft 10 and the cylinder sleeve 20 are eccentrically arranged and the eccentric distance is fixed; the piston sleeve 31 is rotatably arranged in the cylinder sleeve 20, and the piston sleeve 31 has two limiting channels 311, which are sequentially arranged along the axial direction of the rotating shaft 10, and the extending direction of the limiting channels 311 is perpendicular to the axial direction of the rotating shaft 10; the piston 32 has a through hole 321, There are two pistons 32, and the two eccentric parts 11 extend into the two through holes 321 of the two pistons 32 respectively. The two pistons 32 are correspondingly movably arranged in the two limiting channels 311 to form a variable volume chamber, and the variable volume chamber is located in the moving direction of the piston 32. The rotating shaft 10 rotates to drive the piston 32 to move in the limiting channel 311 and interact with the piston sleeve 31 at the same time, so that the piston sleeve 31 and the piston 32 rotate in the cylinder sleeve 20; wherein, the axial projection of the piston 32 in the through hole 321 is circular.

[0068] By optimizing the structure of the piston 32, the axial projection of the piston 32 in the through hole 321 is circular, which simplifies the processing technology of the piston 32 and helps save the manufacturing cost of the pump body assembly, thereby ensuring the economy of the rotary cylinder pump.

[0069] like Figures 1 to 4 As shown, the piston 32 is cylindrical, and the extension direction of the through hole 321 is consistent with the axial direction of the piston 32.

[0070] like Figure 2 As shown, letter F indicates that the piston 32 is in line contact with the limiting channel 311 .

[0071] like Figure 3 and Fig. 22 As shown, the two limiting channels 311 are connected through the central hole 312 .

[0072] like Fig.18 and Fig.19 As shown, the outer diameter D of the piston 32 hs The height H of the piston 32 in its axial direction hs The ratio ranges from 0.5 to 2.

[0073] Preferably, the inner diameter D of the piston 32 is hs2 The outer diameter D of the piston 32 hs The ratio ranges from 0.2 to 0.8.

[0074] Embodiment 2

[0075] like Figures 5 to 10 As shown, the end edge of the piston 32 facing the limiting channel 311 has a rounded corner, and the radius R of the rounded corner is smaller than the height H of the piston 32 in its axial direction.hs , and the radius R of the fillet is smaller than the outer diameter D of the piston 32 hs .

[0076] like Fig.23 As shown, the minimum side thickness L1 of the limiting channel 311 is equal to the outer diameter D of the piston sleeve 31. qw The ratio ranges from 0.05 to 0.3.

[0077] like Fig.21 As shown, the height H of the connection between the two limiting channels 311 in the axial direction of the piston sleeve 31 is q2 The height H of the piston sleeve 31 in the axial direction q1 The ratio ranges from 0.05 to 0.4.

[0078] like Fig.23 As shown, the width W of the limiting channel 311 is q1 , the outer diameter D of the piston 32 hs , the outer diameter D of the piston sleeve 31 qw Between: (W q1 -D hs ) / D qw The value range is 0 to 0.0025.

[0079] Preferably, (W q1 -D hs ) / D qw The value range is 0.0002~0.0007.

[0080] It should be noted that in the present application, the piston 32 has a first chamfer R1 at the edge of the end face facing the limiting channel 311, and a second chamfer R2 is provided between the two channel side walls of the limiting channel 311 and the channel bottom surface of the limiting channel 311. The first chamfer R1 is an annular chamfer opened at the edge of the end face of the piston 32 facing the limiting channel 311, and the second chamfer R2 and the first chamfer R1 satisfy: R1≥R2.

[0081] Optionally, the value range of the first chamfer R1 is 0.2-0.3 mm.

[0082] Optionally, the second chamfer R2 and the first chamfer R1 satisfy: -0.1 mm<R2-R1<0 mm.

[0083] like Figure 2 As shown, the outer peripheral surface of the piston 32 is in line contact with the channel wall of the limiting channel 311, so that the piston 32 is rotatably arranged relative to the piston sleeve 31.

[0084] Embodiment 3

[0085] like Figures 11 to 15As shown, the piston 32 has a third chamfer R3 at the edge of the end surface facing the limiting channel 311, and a fourth chamfer R4 is provided between the two channel side walls of the limiting channel 311 and the channel bottom surface of the limiting channel 311. The third chamfer R3 is a partial chamfer opened at the edge of the end surface of the piston 32 facing the limiting channel 311, and the fourth chamfer R4 and the third chamfer R3 satisfy: R3≥R4.

[0086] It should be noted that, in the present application, the fourth chamfer R4 and the third chamfer R3 satisfy: -0.1mm<R4-R3<0mm.

[0087] It should be noted that, in the present application, the channel cross section of the limiting channel 311 is adapted to the projection of the piston 32 in the extension direction of the limiting channel 311 , so that the piston 32 is slidably disposed in the limiting channel 311 .

[0088] like Fig.15 and Fig.16 As shown, the first sealing distance Q1 between the piston 32 and the piston sleeve 31 is the minimum distance between the outer circumferential edge of the piston 32 and the inner circumferential edge of the piston sleeve 31 , wherein Q1>0.

[0089] Optionally, the value range of the first sealing distance Q1 is 1 to 3 mm.

[0090] Preferably, the first sealing distance Q1 and the outer diameter D of the piston 32 are hs , the inner diameter D1 of the piston sleeve 31 satisfies: Q1=0.5×D hs −0.5×D1−2×e, wherein e is the eccentricity of the eccentric portion 11 .

[0091] It should be noted that in the present application, the piston 32 has a fifth chamfer R5 at the edge of the end face facing the limiting channel 311, and a sixth chamfer R6 is provided between the two channel side walls of the limiting channel 311 and the channel bottom surface of the limiting channel 311. The fifth chamfer R5 is an annular chamfer opened at the edge of the end face of the piston 32 facing the limiting channel 311, and the sixth chamfer R6 and the fifth chamfer R5 satisfy: R5≥R6.

[0092] Optionally, the value range of the fifth chamfer R5 is greater than 0.3 mm.

[0093] Preferably, the sixth chamfer R6 and the fifth chamfer R5 satisfy: -0.1 mm<R6-R5<0 mm.

[0094] It should be noted that, in the present application, the outer peripheral surface of the piston 32 is in line contact with the channel wall of the limiting channel 311 , so that the piston 32 is rotatably arranged relative to the piston sleeve 31 .

[0095] like Fig.15and Fig.17 As shown, the second sealing distance Q2 between the piston 32 and the piston sleeve 31 is the minimum distance between the outer circle edge of the piston 32 and the inner circle edge of the piston sleeve 31, minus the fifth chamfer R5, wherein Q2>0.

[0096] Optionally, the second sealing distance Q2 has a value range of 1 to 3 mm.

[0097] Preferably, the second sealing distance Q2 and the outer diameter D of the piston 32 are hs , the inner diameter D1 of the piston sleeve 31 and the fifth chamfer R5 satisfy: Q2 = 0.5 × D hs -0.5×D1-2×e-R5, wherein e is the eccentricity of the eccentric portion 11.

[0098] It should be noted that in the present application, there is a phase difference of a first angle A between the two eccentric portions 11, the eccentricity of the two eccentric portions 11 is equal, and there is a phase difference of a second angle B between the extension directions of the two limiting channels 311, wherein the first angle A is twice the second angle B.

[0099] Preferably, the two eccentric portions 11 are arranged opposite to each other at an angle of 180°.

[0100] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0101] Unless otherwise specifically stated, the relative arrangement, numerical expressions and numerical values ​​of the parts and steps described in these embodiments do not limit the scope of the utility model. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to the actual proportional relationship. The technology, methods and equipment known to ordinary technicians in the relevant field may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be regarded as a part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once a certain item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0102] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0103] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0104] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the numbers used in this way can be interchanged where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein.

[0105] The above description is only the preferred embodiment of the utility model, and is not intended to limit the utility model. For those skilled in the art, the utility model can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the utility model shall be included in the protection scope of the utility model.

Claims

1. A pump assembly, characterized in that: include: A rotating shaft (10), wherein the rotating shaft (10) is provided with two eccentric parts (11) along its axial direction; The cylinder sleeve (20), the rotating shaft (10) and the cylinder sleeve (20) are eccentrically arranged with a fixed eccentric distance; A piston sleeve (31), the piston sleeve (31) being rotatably disposed in the cylinder sleeve (20), the piston sleeve (31) having two limiting channels (311), the two limiting channels (311) being sequentially disposed along the axial direction of the rotating shaft (10), and the extending direction of the limiting channels (311) being perpendicular to the axial direction of the rotating shaft (10); A piston (32), wherein the piston (32) has a through hole (321), there are two pistons (32), the two eccentric parts (11) extend into the two through holes (321) of the two pistons (32) respectively, the two pistons (32) are movably arranged in the two limiting channels (311) and form a variable volume chamber, the variable volume chamber is located in the moving direction of the piston (32), the rotating shaft (10) rotates to drive the piston (32) to move in the limiting channel (311) and interacts with the piston sleeve (31) so that the piston sleeve (31) and the piston (32) rotate in the cylinder sleeve (20); Wherein, the axial projection of the piston (32) in the through hole (321) is circular.

2. The pump assembly according to claim 1, characterized in that: The piston (32) is cylindrical, and the extending direction of the through hole (321) is consistent with the axial direction of the piston (32).

3. The pump assembly according to claim 1, characterized in that: The outer diameter D of the piston (32) hs The height H of the piston (32) in the axial direction hs The ratio ranges from 0.5 to 2.

4. The pump assembly according to claim 1, characterized in that: The inner diameter D of the piston (32) hs2 The outer diameter D of the piston (32) hs The ratio ranges from 0.2 to 0.

8.

5. The pump assembly according to claim 1, characterized in that: The piston (32) has a rounded corner at the edge of the end surface facing the limiting channel (311), and the radius R of the rounded corner is smaller than the height H of the piston (32) in the axial direction. hs , and the radius R of the fillet is smaller than the outer diameter D of the piston (32) hs .

6. The pump assembly according to claim 1, characterized in that: The minimum side thickness L1 of the limiting channel (311) and the outer diameter D of the piston sleeve (31) are qw The ratio ranges from 0.05 to 0.

3.

7. The pump assembly according to claim 1, characterized in that: The height H of the connection between the two limiting channels (311) in the axial direction of the piston sleeve (31) is q2 The height H of the piston sleeve (31) in the axial direction q1 The ratio ranges from 0.05 to 0.

4.

8. The pump assembly according to claim 1, characterized in that: The width W of the limiting channel (311) q1 , the outer diameter D of the piston (32) hs , the outer diameter D of the piston sleeve (31) qw Between: (W q1 -D hs ) / D qw The value range is 0 to 0.0025.

9. The pump assembly according to claim 8, characterized in that: (W q1 -D hs ) / D qw The value range is 0.0002~0.0007.

10. The pump assembly according to claim 1, characterized in that: The piston (32) has a first chamfer R1 at the edge of the end surface facing the limiting channel (311), and a second chamfer R2 is provided between the two channel side walls of the limiting channel (311) and the channel bottom surface of the limiting channel (311). The first chamfer R1 is an annular chamfer provided at the edge of the end surface of the piston (32) facing the limiting channel (311), and the second chamfer R2 satisfies the first chamfer R1: R1≥R2.

11. The pump assembly according to claim 10, characterized in that: The value range of the first chamfer R1 is 0.2-0.3 mm.

12. The pump assembly according to claim 10, characterized in that The second chamfer R2 and the first chamfer R1 satisfy the following relationship: -0.1 mm<R2-R1<0 mm.

13. The pump assembly according to claim 10, characterized in that: The outer peripheral surface of the piston (32) is in line contact with the channel wall of the limiting channel (311), so that the piston (32) is rotatably arranged relative to the piston sleeve (31).

14. The pump assembly according to claim 1, characterized in that The piston (32) has a third chamfer R3 at the edge of the end surface facing the limiting channel (311), and a fourth chamfer R4 is provided between the two channel side walls of the limiting channel (311) and the channel bottom surface of the limiting channel (311). The third chamfer R3 is a partial chamfer provided at the edge of the end surface of the piston (32) facing the limiting channel (311), and the fourth chamfer R4 and the third chamfer R3 satisfy the following relationship: R3≥R4.

15. The pump assembly according to claim 14, characterized in that The fourth chamfer R4 and the third chamfer R3 satisfy the following relationship: -0.1 mm<R4-R3<0 mm.

16. The pump assembly according to claim 14, characterized in that The channel cross section of the limiting channel (311) is adapted to the projection of the piston (32) in the extension direction of the limiting channel (311), so that the piston (32) is slidably disposed in the limiting channel (311).

17. The pump assembly according to claim 10 or 14, characterized in that: The first sealing distance Q1 between the piston (32) and the piston sleeve (31) is the minimum distance between the outer circle edge of the piston (32) and the inner circle edge of the piston sleeve (31), wherein Q1>0.

18. The pump assembly according to claim 17, characterized in that The value range of the first sealing distance Q1 is 1 to 3 mm.

19. The pump assembly according to claim 17, characterized in that The first sealing distance Q1 and the outer diameter D of the piston (32) hs , the inner diameter D1 of the piston sleeve (31) satisfies: Q1 = 0.5 × D hs -0.5×D1-2×e, wherein e is the eccentricity of the eccentric portion (11).

20. The pump assembly according to claim 1, characterized in that The piston (32) has a fifth chamfer R5 at the edge of the end surface facing the limiting channel (311), and a sixth chamfer R6 is provided between the two channel side walls of the limiting channel (311) and the channel bottom surface of the limiting channel (311). The fifth chamfer R5 is an annular chamfer provided at the edge of the end surface of the piston (32) facing the limiting channel (311), and the sixth chamfer R6 satisfies the fifth chamfer R5: R5≥R6.

21. The pump assembly according to claim 20, characterized in that The value range of the fifth chamfer R5 is greater than 0.3 mm.

22. The pump assembly according to claim 20, characterized in that The sixth chamfer R6 and the fifth chamfer R5 satisfy the following relationship: -0.1 mm<R6-R5<0 mm.

23. The pump assembly according to claim 20, characterized in that The outer peripheral surface of the piston (32) is in line contact with the channel wall of the limiting channel (311), so that the piston (32) is rotatably arranged relative to the piston sleeve (31).

24. The pump assembly according to claim 20, characterized in that The second sealing distance Q2 between the piston (32) and the piston sleeve (31) is the minimum distance between the outer circle edge of the piston (32) and the inner circle edge of the piston sleeve (31), minus the fifth chamfer R5, wherein Q2>0.

25. The pump assembly according to claim 24, characterized in that The second sealing distance Q2 has a value range of 1 to 3 mm.

26. The pump assembly according to claim 24, characterized in that The second sealing distance Q2, the outer diameter D of the piston (32) hs , the inner diameter D1 of the piston sleeve (31) and the fifth chamfer R5 satisfy: Q2 = 0.5 × D hs -0.5×D1-2×e-R5, wherein e is the eccentricity of the eccentric portion (11).

27. The pump assembly according to claim 1, characterized in that There is a phase difference of a first angle A between the two eccentric portions (11), the eccentricity of the two eccentric portions (11) is equal, and there is a phase difference of a second angle B between the extension directions of the two limiting channels (311), wherein the first angle A is twice the second angle B.

28. The pump assembly according to claim 27, characterized in that The two eccentric parts (11) are arranged opposite to each other at an angle of 180 degrees.

29. A rotary cylinder pump, characterized in that: It comprises a pump body assembly, and the pump body assembly is the pump body assembly according to any one of claims 1 to 28.

30. A heat exchange device, characterized in that: It comprises a rotary cylinder pump, wherein the rotary cylinder pump is the rotary cylinder pump according to claim 29.

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