Pump body assembly and fluid machine

Abstract

This invention provides a pump body assembly and a fluid machine. The pump body assembly includes: a cylinder liner having a volumetric cavity; a cylinder rotatably disposed within the volumetric cavity, with the rotation center of the cylinder coinciding with the center of the volumetric cavity; the outer peripheral surface of the cylinder fitting into the inner surface of the cylinder liner; the outer peripheral surface of the cylinder serving as a first contact surface; and the inner surface of the cylinder liner serving as a second contact surface; the first and second contact surfaces forming a friction pair surface; and a textured structure provided on the first and / or second contact surfaces. The pump body assembly of this invention solves the problem of easy wear between the cylinder and the cylinder liner.

Description

Technical Field

[0001] This invention relates to the technical field of rotary cylinder compressors, and more specifically, to a pump assembly and fluid machinery. Background Technology

[0002] Taking rotary cylinder compressors as an example, the increase in mechanical power consumption of rotary cylinder compressors is greater than that of rotary compressors when the operating frequency increases, which affects the compressor's energy efficiency. At the same time, rotary cylinder compressors have more friction pairs in the pump body, which places higher demands on fluid lubrication. Poor lubrication may lead to reliability problems.

[0003] The cylinder is installed inside the cylinder liner and moves in a circular motion relative to the cylinder liner. Due to the large contact area between the cylinder and the cylinder liner, significant friction occurs between them during actual compressor operation, increasing mechanical power consumption and wear. Furthermore, both the outer circumferential surface of the cylinder and the inner circumferential surface of the cylinder liner form the sealing surfaces of the compression chamber; friction between the cylinder and the cylinder liner can damage the sealing performance of these surfaces.

[0004] As can be seen from the above, the cylinder and cylinder liner of the rotary compressor currently generate a lot of friction, which leads to damage to the cylinder and cylinder liner and also disrupts the sealing between the cylinder and cylinder liner. Summary of the Invention

[0005] The main objective of this invention is to provide a pump body assembly and fluid machinery to solve the problems in the prior art where the cylinder and cylinder liner of a rotary compressor generate large friction, resulting in damage to the cylinder and cylinder liner and destruction of the sealing between the cylinder and cylinder liner.

[0006] To achieve the above objectives, according to one aspect of the present invention, a pump body assembly is provided, including a cylinder liner having a volumetric cavity; a cylinder rotatably disposed within the volumetric cavity, wherein the rotation center of the cylinder coincides with the center of the volumetric cavity, the outer peripheral surface of the cylinder is adapted to the inner surface of the cylinder liner, the outer peripheral surface of the cylinder is a first contact surface, the inner surface of the cylinder liner is a second contact surface, the first contact surface and the second contact surface constitute a friction pair surface, and a textured structure is provided on the first contact surface and / or the second contact surface.

[0007] Furthermore, the textured structure consists of multiple spaced textured grooves; or the textured structure consists of multiple intersecting textured grooves, with the multiple intersecting textured grooves forming a mesh textured structure.

[0008] Furthermore, when the textured structure is composed of multiple spaced textured grooves, the groove openings are elliptical, circular, or polygonal; when the textured structure is composed of multiple intersecting textured grooves, each textured groove is a straight groove, a curved groove, or a polygonal groove.

[0009] Furthermore, when the opening of the textured groove is circular, the equivalent diameter of the textured groove is 0.02 mm to 0.5 mm.

[0010] Furthermore, when the textured structure consists of multiple intersecting textured grooves, the width of the textured grooves is 0.02 mm to 0.5 mm.

[0011] Furthermore, when the groove opening of the textured groove is elliptical, the minor axis a and the major axis b of the ellipse satisfy the following condition: 1.5 ≤ b / a ≤ 3.5.

[0012] Furthermore, the range of values ​​for the minor axis a of the ellipse is 0.008 mm ≤ a ≤ 0.05 mm; and / or the range of values ​​for the major axis b of the ellipse is 0.016 mm ≤ b ≤ 0.1 mm.

[0013] Furthermore, when the groove opening of the textured groove is elliptical, the center distance k between two adjacent ellipses and the major axis b of the ellipse satisfy the following condition: 2.5≤k / b≤5.

[0014] Furthermore, the friction pair gap L between the first contact surface and the second contact surface satisfies the following relationship with the depth H of the textured groove: H / L is 0.4 to 0.8.

[0015] Furthermore, the area S of the friction pair surface and the total area S1 of the region where the texture structure is located satisfy the following relationship: S1 / S is 5% to 15%.

[0016] Furthermore, when the textured structure consists of multiple spaced textured grooves, the centerline of the textured structure is perpendicular to the rotation centerline of the cylinder.

[0017] Furthermore, the first contact surface has a textured structure, and the distance L from the area where the textured structure is located to the edge of the first contact surface in the direction of the rotation center line of the cylinder is greater than or equal to 2.5 mm.

[0018] Furthermore, a piston hole is provided on the cylinder along its radial direction, and a textured structure is provided on the first contact surface. The radius Rb of the textured structure at the edge of the piston hole satisfies the condition that Rb-Ra is greater than or equal to 2.5mm.

[0019] Furthermore, at least a portion of the first contact surface is provided with a textured structure; and / or at least a portion of the second contact surface is provided with a textured structure.

[0020] Furthermore, a textured structure is provided at all points on the first contact surface; a textured structure is provided in a portion of the second contact surface.

[0021] Furthermore, the cylinder liner has an intake passage and an exhaust passage, with the intake passage located on the intake side of the cylinder liner and the exhaust passage located on the exhaust side of the cylinder liner, and no textured structure is provided on the area of ​​the second contact surface located on the intake side.

[0022] According to another aspect of the present invention, a fluid machine is provided including a pump body assembly.

[0023] According to the technical solution of the present invention, the pump body assembly includes a cylinder liner and a cylinder, the cylinder liner having a volumetric cavity; the cylinder is rotatably disposed in the volumetric cavity, and the rotation center of the cylinder coincides with the center of the volumetric cavity, the outer peripheral surface of the cylinder is adapted to the inner surface of the cylinder liner, the outer peripheral surface of the cylinder is a first contact surface, the inner surface of the cylinder liner is a second contact surface, the first contact surface and the second contact surface constitute a friction pair surface, and a textured structure is provided on the first contact surface and / or the second contact surface.

[0024] As can be seen from the above description, in the embodiments of the present invention, by providing a textured structure on the contact surface of the cylinder and cylinder liner, the textured structure can reduce the frictional area between the cylinder and cylinder liner, reduce the frictional force between the cylinder and cylinder liner, and avoid the problem of damage to parts and impact on the sealing performance of the cylinder and cylinder liner due to friction between the cylinder and cylinder liner. Currently, the contact area between the cylinder and cylinder liner of the pump body is large. During the actual operation of the compressor, significant friction occurs between the cylinder and cylinder liner, increasing mechanical power consumption and wear. Simultaneously, both the outer circumferential surface of the cylinder and the inner circumferential surface of the cylinder liner are sealing surfaces that constitute the sealed compression chamber; friction between the cylinder and cylinder liner can damage the sealing performance of these surfaces.

[0025] Specifically, the cylinder rotates circumferentially within the cylinder liner's cavity, forming a friction pair with the cylinder. A textured structure is created on the contact surface between the cylinder and cylinder liner. This textured structure reduces the contact area between the cylinder and cylinder liner. During operation, oil from the gaps between the friction pair surfaces enters the textured structure. During the relative movement of the cylinder and cylinder liner, the load-bearing capacity of the fluid film formed by the oil is enhanced, causing the surfaces of the two contact surfaces to tend to separate, reducing friction. The formed fluid film is more stable and tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between the cylinder and cylinder liner. Attached Figure Description

[0026] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0027] Figure 1 A schematic diagram showing the installation relationship between the cylinder and cylinder liner in this invention is provided; and

[0028] Figure 2 It shows Figure 1 A schematic diagram of a textured structure on the first contact surface of the cylinder.

[0029] Figure 3 It shows Figure 2 A schematic diagram of the unfolded structure of the first contact surface of the middle cylinder;

[0030] Figure 4 It shows Figure 3 Enlarged view of point G0 in the middle;

[0031] Figure 5 A schematic diagram of the textured structure formed on the second contact surface of the cylinder liner in this invention is shown.

[0032] Figure 6 A schematic diagram showing the installation relationship between the limiting plate and the cylinder in this invention is provided; and

[0033] Figure 7 A schematic diagram of a textured structure on the limiting protrusion ring of the cylinder in this invention is shown, wherein the opening of the textured structure is elliptical.

[0034] Figure 8 It shows Figure 7 Sectional view along line W1-W1;

[0035] Figure 9 It shows Figure 7 Enlarged view at Z1;

[0036] Figure 10 A schematic diagram of a textured structure on the limiting protrusion ring of the cylinder in this invention is shown, wherein the opening of the textured structure is circular;

[0037] Figure 11 It shows Figure 10 Sectional view along line W2-W2;

[0038] Figure 12 It shows Figure 10 Enlarged view at Z2;

[0039] Figure 13 A schematic diagram is shown of a textured structure formed on the wall of the upper limit hole of the upper limit plate in this invention, wherein the opening of the textured structure is elliptical.

[0040] Figure 14 It shows Figure 13 Sectional view along line W3-W3;

[0041] Figure 15 It shows Figure 14 Enlarged view at Z3 in the middle;

[0042] Figure 16A schematic diagram is shown of a textured structure formed on the wall of the upper limit hole of the upper limit plate in this invention, wherein the opening of the textured structure is circular;

[0043] Figure 17 It shows Figure 16 Sectional view along line W4-W4;

[0044] Figure 18 It shows Figure 17 Enlarged view at Z4 in the middle;

[0045] Figure 19 A schematic diagram is shown of a textured structure formed on the wall of the lower limiting hole of the lower limiting plate in this invention, wherein the opening of the textured structure is elliptical.

[0046] Figure 20 It shows Figure 19 Sectional view along line W5-W5;

[0047] Figure 21 It shows Figure 20 Enlarged view at Z5 in the middle;

[0048] Figure 22 A schematic diagram is shown of a textured structure formed on the wall of the lower limiting hole of the lower limiting plate in this invention, wherein the opening of the textured structure is circular;

[0049] Figure 23 It shows Figure 22 Sectional view along line W6-W6;

[0050] Figure 24 It shows Figure 23 Enlarged view of Z6 in the middle;

[0051] Figure 25 A schematic diagram of a textured structure on the end face of the cylinder in this invention is shown, wherein the textured structure is a spiral groove;

[0052] Figure 26 It shows the relationship with Figure 25 A schematic diagram of the textured structure on the upper limit plate used in conjunction with the device, wherein the textured structure is a spiral groove;

[0053] Figure 27 It shows Figure 26 Sectional view along line W7-W7;

[0054] Figure 28 It shows the relationship with Figure 25 A schematic diagram of the textured structure on the lower limit plate used in conjunction with the device, wherein the textured structure is a spiral groove;

[0055] Figure 29 A schematic diagram of a textured structure on the upper limit plate in this invention is shown, wherein the textured structure is an arc groove;

[0056] Figure 30 It shows the relationship with Figure 29 A schematic diagram of the textured structure on the end face of the cylinder used in conjunction with the cylinder, wherein the textured structure is a circular arc groove;

[0057] Figure 31 A schematic diagram of the textured structure on the upper limit plate in this invention is shown, wherein the textured structure is a combination of straight grooves and micropores;

[0058] Figure 32 A schematic diagram of the textured structure on the cylinder in this invention is shown, wherein the textured structure is a combination of straight grooves and micropores;

[0059] Figure 33 It shows Figure 32 Enlarged view of Z7 in the middle;

[0060] Figure 34 A schematic diagram illustrating the installation relationship between the piston and cylinder according to the present invention is shown; and

[0061] Figure 35 A schematic diagram of the mounting structure of the rotating shaft, piston, and cylinder according to the present invention is shown;

[0062] Figure 36 A schematic diagram is shown showing that the entire area of ​​the second contact surface of the piston in this invention has a textured structure.

[0063] Figure 37 It shows the relationship with Figure 36 The schematic diagram of the piston-operated cylinder is shown in the figure. The entire area of ​​the first contact surface of the cylinder is provided with a textured structure.

[0064] Figure 38 It shows Figure 36 Piston and Figure 37 A radial sectional view of the cylinder assembly in the middle;

[0065] Figure 39 It shows Figure 36 Piston and Figure 37 Axial sectional view of the cylinder assembly in the middle;

[0066] Figure 40 A schematic diagram showing the textured structure formed on the first and third regions of the second contact surface of the piston in this invention is shown.

[0067] Figure 41 It shows the relationship with Figure 40 A schematic diagram of the structure of a cylinder that engages with a piston, wherein a textured structure is provided on the fifth region surface and the seventh region surface of the first contact surface of the cylinder.

[0068] Figure 42A schematic diagram showing the textured structure formed on the second region surface and the fourth region surface of the piston's second contact surface in this invention is shown.

[0069] Figure 43 It shows the relationship with Figure 42 A schematic diagram of the structure of a cylinder that engages with a piston, wherein a textured structure is provided on the sixth region surface and the eighth region surface of the first contact surface of the cylinder.

[0070] Figure 44 An exploded view of the pump body assembly of the present invention is shown; and

[0071] Figure 45 It shows Figure 44 A schematic diagram showing the installation relationship between the rotating shaft and the piston.

[0072] Figure 46 A schematic diagram of a textured structure on the second contact surface of the rotating shaft in this invention is shown, wherein the textured structure is elliptical.

[0073] Figure 47 It shows Figure 46 Enlarged view of point S0 in the image;

[0074] Figure 48 A schematic diagram of a textured structure on the second contact surface of the rotating shaft in this invention is shown, wherein the textured structure is circular;

[0075] Figure 49 It shows Figure 48 Enlarged view of point S1 in the image;

[0076] Figure 50 A schematic diagram of a textured structure on the second contact surface of the rotating shaft in this invention is shown, wherein the textured structure is polygonal;

[0077] Figure 51 It shows Figure 50 Enlarged view of point S2 in the image;

[0078] Figure 52 A top view of the piston in this invention is shown;

[0079] Figure 53 It shows Figure 52 A cross-sectional view along line C1-C1, where the texture is elliptical;

[0080] Figure 54 It shows Figure 53 Enlarged view of point S3 in the middle;

[0081] Figure 55 A schematic diagram of the piston structure in this invention is shown;

[0082] Figure 56 It shows Figure 55 A cross-sectional view along line C2-C2, where the texture is circular;

[0083] Figure 57 It shows Figure 56 Enlarged view of point S4 in the middle;

[0084] Figure 58 An exploded view of the pump body assembly in the invention is shown; and

[0085] Figure 59 It shows Figure 58 A schematic diagram showing the installation relationship between the rotating shaft and the flange structure.

[0086] Figure 60 A schematic diagram is shown showing that the entire area of ​​the second contact surface of the rotating shaft in this invention has a textured structure, wherein the opening of the textured structure is elliptical;

[0087] Figure 61 It shows Figure 60 A magnified view of a section at point B in the middle;

[0088] Figure 62 It shows Figure 60 A magnified view of a section at point C;

[0089] Figure 63 It shows Figure 60 Sectional view along the middle AA direction;

[0090] Figure 64 It shows Figure 63 A magnified view of a section at point D;

[0091] Figure 65 A schematic diagram is shown of a textured structure formed on the second region surface of the second contact surface of the rotating shaft in this invention, wherein the opening of the textured structure is elliptical.

[0092] Figure 66 It shows Figure 65 A magnified view of point E in the image;

[0093] Figure 67 A schematic diagram is shown of a textured structure formed on the surface of the first region of the second contact surface of the rotating shaft in this invention, wherein the opening of the textured structure is elliptical.

[0094] Figure 68 It shows Figure 67 A magnified view of a section at point F in the middle;

[0095] Figure 69 A schematic diagram is shown showing that the entire area of ​​the second contact surface of the rotating shaft in this invention has a textured structure, wherein the opening of the textured structure is circular;

[0096] Figure 70It shows Figure 69 A magnified view of point G in the image;

[0097] Figure 71 A schematic diagram is shown of a textured structure formed on the surface of the first region of the second contact surface of the rotating shaft in this invention, wherein the opening of the textured structure is circular;

[0098] Figure 72 It shows Figure 71 A magnified view of a section at point J;

[0099] Figure 73 A schematic diagram is shown of a textured structure formed on the second region surface of the second contact surface of the rotating shaft in this invention, wherein the opening of the textured structure is circular;

[0100] Figure 74 It shows Figure 73 A magnified view of a portion of point O in the middle;

[0101] Figure 75 A top view of the upper flange in this invention is shown, wherein the opening of the textured structure is elliptical;

[0102] Figure 76 It shows Figure 75 Cross-sectional view along the KK axis;

[0103] Figure 77 It shows Figure 76 Enlarged view at point M;

[0104] Figure 78 A top view of the upper flange in this invention is shown, wherein the opening of the textured structure is circular;

[0105] Figure 79 It shows Figure 78 Sectional view along line K1-K1;

[0106] Figure 80 It shows Figure 79 Enlarged view of point M1;

[0107] Figure 81 A top view of the lower flange of the present invention is shown, wherein the opening of the texture structure is elliptical;

[0108] Figure 82 It shows Figure 81 Sectional view along line K2-K2;

[0109] Figure 83 It shows Figure 82 Enlarged view of section S in the middle;

[0110] Figure 84 A top view of the lower flange of the present invention is shown, wherein the opening of the texture structure is circular;

[0111] Figure 85 It shows Figure 84 Sectional view along line K3-K3;

[0112] Figure 86 It shows Figure 85 Enlarged view of point S1 in the middle.

[0113] The above figures include the following reference numerals:

[0114] 10. Cylinder; 1001. First contact surface; 101. Fifth region surface; 102. Sixth region surface; 103. Seventh region surface; 104. Eighth region surface; 105. Cylinder texture structure; 106. Piston bore; 1011. Limiting protrusion ring; 20. Piston; 2001. First contact surface; 201. First region surface; 202. Second region surface; 203. Third region surface; 204. Fourth region surface; 205. Piston texture structure; 30. Rotating shaft; 3001. Second contact surface; 301. First region surface; 302, Second region surface; 40, Cylinder liner; 4001, Volumetric cavity; 4002, Second contact surface; 50, Upper flange; 501, Third region surface; 60, Lower flange; 601, Fourth region surface; 70, Upper limit plate; 7001, Upper limit hole; 80, Lower limit plate; 8001, Lower limit hole; 100, Texture structure. Detailed Implementation

[0115] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0116] It should be noted that, unless otherwise specified, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0117] In this invention, unless otherwise stated, directional terms such as "upper," "lower," "top," and "bottom" are generally used in relation to the direction shown in the accompanying drawings, or in relation to the vertical, perpendicular, or gravitational direction of the component itself; similarly, for ease of understanding and description, "inner" and "outer" refer to the inner and outer contours of each component itself, but the above directional terms are not intended to limit this invention.

[0118] To address the problems of excessive friction in the pump body assembly of existing rotary cylinder compressors during operation, which leads to damage to the pump body assembly and compromises its sealing performance, this application provides a pump body assembly and fluid machinery.

[0119] The fluid machinery includes the pump assembly described below. Specifically, the fluid machinery is a compressor. Further, the compressor is a rotary compressor.

[0120] To address the issues of excessive friction in the pump body assembly of existing rotary cylinder compressors during operation, which leads to damage and compromises the pump body assembly's sealing performance, a textured structure 100 can be provided on the contact surface between the cylinder liner 40 and the cylinder 10. This reduces the friction between the cylinder 10 and the cylinder liner 40, thereby improving their sealing performance.

[0121] Specifically, such as Figures 1 to 5 As shown, the pump body assembly includes a cylinder liner 40 and a cylinder 10. The cylinder liner 40 has a volumetric cavity 4001. The cylinder 10 is rotatably disposed in the volumetric cavity 4001, and the rotation center of the cylinder 10 coincides with the center of the volumetric cavity 4001. The outer peripheral surface of the cylinder 10 is adapted to the inner surface of the cylinder liner 40. The outer peripheral surface of the cylinder 10 is a first contact surface 1001, and the inner surface of the cylinder liner 40 is a second contact surface 4002. The first contact surface 1001 and the second contact surface 4002 form a friction pair surface. A textured structure 100 is provided on the first contact surface 1001 and / or the second contact surface 4002.

[0122] As can be seen from the above description, by providing a textured structure 100 on the contact surface of the cylinder 10 and the cylinder liner 40, the textured structure 100 can reduce the frictional area between the cylinder 10 and the cylinder liner 40, reduce the frictional force between the cylinder 10 and the cylinder liner 40, and avoid the problem of parts being damaged and the sealing performance between the cylinder 10 and the cylinder liner 40 being affected by friction. Currently, the contact area between the cylinder 10 and the cylinder liner 40 of the pump body is large. During the actual operation of the compressor, a large amount of friction will be generated between the cylinder 10 and the cylinder liner 40, increasing mechanical power consumption and wear. At the same time, the outer peripheral surface of the cylinder 10 and the inner peripheral surface of the cylinder liner 40 are both sealing surfaces that constitute the sealed compression chamber. Friction between the cylinder 10 and the cylinder liner 40 can damage the sealing performance of the sealing surfaces.

[0123] Specifically, the cylinder 10 rotates circumferentially within the volume chamber 4001 of the cylinder liner 40. The cylinder 10 and the cylinder liner 40 form a friction pair. A textured structure 100 is formed on the contact surface between the cylinder 10 and the cylinder liner 40. The textured structure 100 reduces the contact area between the cylinder 10 and the cylinder liner 40. During the movement, oil in the gap between the surfaces of the friction pair enters the interior of the textured structure 100. During the relative movement between the cylinder 10 and the cylinder liner 40, the load-bearing capacity of the fluid film formed by the oil is enhanced, causing the surfaces of the two contact surfaces to tend to separate, reducing friction. The formed fluid film is more stable and tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between the cylinder 10 and the cylinder liner 40.

[0124] It should be noted that, in Figures 1 to 5 The specific embodiments shown illustrate schemes for providing the textured structure 100 on both the cylinder 10 and the cylinder liner 40. In specific embodiments, the textured structure 100 can be provided on both the cylinder 10 and the cylinder liner 40 simultaneously, or it can be provided on only one of the two. Since there are many possible combinations, they will not be listed individually. Different accompanying drawings will be provided below to illustrate the different forms of the textured structure 100.

[0125] like Figures 1 to 5 As shown, the texture structure 100 consists of multiple spaced-apart textured grooves. Specifically, the texture structure 100 can be composed of spaced-apart, non-connected structures.

[0126] Specifically, when the textured structure 100 is composed of multiple spaced textured grooves, the centerline of the textured structure 100 is perpendicular to the rotation centerline of the cylinder 10. This is beneficial for strengthening the dynamic pressure effect between the cylinder 10 and the cylinder liner 40, increasing the load-bearing capacity and stability of the fluid film between the cylinder 10 and the cylinder liner 40, reducing wear between the cylinder 10 and the cylinder liner 40, and increasing lubrication performance.

[0127] It should be noted that when the texture structure 100 is composed of multiple texture grooves arranged at intervals, the groove openings of the texture grooves are one or more of the following shapes: elliptical, circular, and polygonal.

[0128] Specifically, the grooves of the textured grooves can be elliptical, circular, or polygonal, arranged at intervals, or textured grooves with multiple different shapes can be arranged at intervals. Specifically, the polygon is rhomboid.

[0129] Below, based on the different groove shapes of the textured grooves opened on the cylinder 10 and cylinder liner 40, the following are provided: Figures 1 to 5 Multiple implementation methods.

[0130] like Figures 2 to 4 In the specific embodiment shown, the texture structure 100 is disposed on the cylinder 10. When the texture structure 100 is composed of multiple texture grooves arranged at intervals, the opening of the texture groove is elliptical.

[0131] like Figure 4As shown, the range of the minor axis *a* of the ellipse is 0.008 mm ≤ *a* ≤ 0.05 mm, and the range of the major axis *b* is 0.016 mm ≤ *b* ≤ 0.1 mm. The major and minor axes of the ellipse are within these ranges, and the ratio 1.5 ≤ *b* / *a* ≤ 3.5 is maintained. When the values ​​of the minor and major axes are too large, the strength of the cylinder 10 and cylinder liner 40 decreases due to the excessively large elliptical textured grooves, affecting their service life. Furthermore, excessively large elliptical textured grooves will store excess oil, which is detrimental to fluid film strength and causes oil waste. When the values ​​of the minor and major axes are too small, the amount of oil stored in the textured grooves is insufficient, which is detrimental to enhancing the fluid film's load-bearing capacity. Conversely, excessively small textured grooves cannot store trace amounts of oil, which is detrimental to improving lubrication performance.

[0132] Furthermore, when the groove opening of the textured groove is elliptical, the ratio between the minor axis a and the major axis b of the ellipse satisfies: 1.5 ≤ b / a ≤ 3.5. When the ratio between the major and minor axes of the ellipse is within the range of 1.5 to 3.5, the dynamic pressure effect of the textured area is enhanced during the relative movement of the cylinder 10 and the cylinder liner 40. This strengthens the load-bearing capacity of the fluid film formed on the contact surface between the cylinder 10 and the cylinder liner 40, improving the lubrication performance between them and reducing frictional loss.

[0133] like Figure 4 As shown, when the groove opening of the groove is elliptical, the center distance k between two adjacent ellipses and the major axis b of the ellipse satisfy the following condition: 2.5≤k / b≤5.

[0134] Specifically, the ratio of the center distance between two adjacent ellipses to the major axis of the ellipse is between 2.5 and 5. The spacing between the two adjacent ellipses is set by controlling the center distance *k*. Controlling the ratio of the center distance to the major axis of the ellipse further restricts the relationship between the size of the ellipse and the spacing between them. When the center distance *k* is too large, the gap between the adjacent elliptical grooves increases, resulting in a sparse distribution of the texture structure 100. This sparse texture structure 100 fails to effectively reduce the friction area, and the stability of the fluid film between the cylinder 10 and the cylinder liner 40 is not significantly enhanced, thus failing to effectively reduce the friction between the cylinder 10 and the cylinder liner 40, and also hindering the improvement of the sealing performance between them. When the major axis of the ellipse is too large, the elliptical structure becomes too large, storing excessive oil and hindering the enhancement of the fluid film's load-bearing capacity, thus failing to reduce the friction between the cylinder 10 and the cylinder liner 40.

[0135] Besides being elliptical, the opening of the textured groove can also be other shapes. In a specific embodiment not shown, the textured structure 100 is disposed on the cylinder 10, and when the textured structure 100 is composed of a plurality of spaced textured grooves, the opening of the textured groove is circular.

[0136] Specifically, the equivalent diameter of the textured groove is between 0.02 mm and 0.5 mm. The size of the textured groove should be controlled within the range of 0.02 mm to 0.5 mm. An equivalent diameter that is too small or too large will affect the formation of the fluid film and its specific technical performance. Specifically, if the equivalent diameter is too small, the oil storage capacity inside the textured groove is low, which is not conducive to enhancing the fluid film's load-bearing capacity. At the same time, a textured groove that is too small cannot store trace amounts of wear debris and impurities brought by the oil. If the equivalent diameter is too large, it leads to a reduction in the pump body's strength, service life, and safety.

[0137] In addition to providing a textured structure 100 on the cylinder 10, a textured structure 100 can also be provided on the cylinder liner 40. Specifically, in Figure 5 In the specific embodiment shown, the textured structure 100 is disposed on the cylinder liner 40, and the textured structure 100 is composed of a plurality of spaced textured grooves. Similarly, the opening of the textured grooves can also be circular or elliptical, and the specific setting parameters can be referred to the aforementioned scheme.

[0138] In addition to the above-described embodiments, the texture structure 100 may also consist of multiple intersecting texture grooves, which together form a mesh texture structure (not shown in the figure).

[0139] When the texture structure 100 is composed of multiple intersecting texture grooves, each texture groove is one or more of straight grooves, curved grooves, and zigzag grooves. Specifically, when the texture structure 100 has an intersecting texture groove structure, the texture grooves are all of one type of straight groove, curved groove, and zigzag groove, or they can be a combination of straight grooves, curved grooves, and zigzag grooves.

[0140] Optionally, when the textured structure 100 consists of multiple intersecting textured grooves, the width of the textured grooves is between 0.02 mm and 0.5 mm. Specifically, if the width of the textured groove is too small, the oil storage capacity inside the textured groove is small, which is not conducive to enhancing the fluid film's load-bearing capacity. At the same time, textured grooves with too small a width cannot store trace amounts of wear debris and impurities brought by the oil. If the width of the textured groove is too large, it leads to a reduction in the strength of the pump body, as well as a reduction in service life and safety.

[0141] It should be noted that the arrangement of the texture structure 100 is not limited to the above situation. The arrangement of the texture structure 100 can also be other technical solutions that can achieve the technical effect of reducing friction and increasing sealing.

[0142] The friction pair clearance L between the first contact surface 1001 and the second contact surface 4002 and the depth H of the textured groove satisfy the following condition: H / L is 0.4 to 0.8. Wherein, the friction pair clearance L is greater than the depth H of the textured groove. If the friction pair clearance L is too small, the friction between the first contact surface 1001 and the second contact surface 4002 will intensify; if the depth H of the textured groove is too small, the lubrication of the first contact surface 1001 and the second contact surface 4002 will decrease, making it difficult to store lubricating oil; if the friction pair clearance L is too large, the fluid oil film's carrying capacity will decrease; if the depth H of the textured groove is too large, it will affect the structural strength of the second contact surface 4002 and reduce the hydrodynamic lubrication effect. If the difference between the friction pair clearance L and the depth H of the textured groove is too large, it will negatively affect the lubrication effect of the friction pair surface.

[0143] The area S of the friction pair surface and the total area S1 of the region where the textured structure 100 is located satisfy the following relationship: S1 / S is 5% to 10%. The total area of ​​the region where the textured structure 100 is located includes the area of ​​all textured structures 100. If the textured structure 100 is located in only one region, the total area is the total area of ​​the textured structures 100 in that region. If the textured structure 100 is located in multiple regions, the total area is the sum of the areas of textured structures 100 in all regions. If the proportion of the total area S1 of the region where the textured structure 100 is located is too large, it will affect the overall structural strength of the cylinder liner 40 or the cylinder 10. Simultaneously, if the textured hole is too small, it will not achieve the effect of reducing friction. If the proportion of the total area S1 of the region where the textured structure 100 is located is too small, it will increase friction and wear under load conditions, and also increase the clearance size, affecting sealing performance.

[0144] like Figure 3 As shown, the first contact surface 1001 has a textured structure 100, and the distance L from the area where the textured structure 100 is located to the edge of the first contact surface 1001 in the direction of the rotation center line of the cylinder 10 is greater than or equal to 2.5 mm. When the distance L is less than 2.5 mm, the area of ​​the textured structure 100 is not conducive to the strength of the cylinder 10, and the installation is also not conducive when the distance L is less than 2.5 mm.

[0145] like Figures 1 to 3 As shown, a piston hole 106 is formed radially on the cylinder 10, and a textured structure 100 is provided on the first contact surface 1001. The radius Rb of the area of ​​the textured structure 100 at the edge of the piston hole 106 satisfies the condition that Rb-Ra is greater than or equal to 2.5mm. Specifically, when Rb-Ra is less than 2.5mm, it is not conducive to the use of the cylinder 10 and the cylinder liner 40 and the strength of the cylinder 10, while also increasing the processing technology and wasting processing costs.

[0146] It should be noted that the cylinder liner 40 has an intake passage and an exhaust passage. The intake passage is located on the intake side of the cylinder liner 40, and the exhaust passage is located on the exhaust side of the cylinder liner 40. The second contact surface 4002 is located on the intake side without a textured structure 100. The cylinder 10 moves in a relatively circular motion relative to the cylinder liner 40. During the rotation of the cylinder 10, the intake and exhaust processes are realized through the connection of the intake passage or the connection of the exhaust passage.

[0147] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects:

[0148] In the above embodiments of the present invention, by providing a textured structure 100 on the contact surface of the cylinder 10 and the cylinder liner 40, the textured structure 100 can reduce the frictional area between the cylinder 10 and the cylinder liner 40, reduce the frictional force between the cylinder 10 and the cylinder liner 40, and avoid the problem of damage to parts and impact on the sealing performance of the cylinder 10 and the cylinder liner 40 due to friction between them. Currently, the contact area between the cylinder 10 and the cylinder liner 40 of the pump body is large. During the actual operation of the compressor, a large amount of friction will occur between the cylinder 10 and the cylinder liner 40, increasing mechanical power consumption and wear. At the same time, the outer peripheral surface of the cylinder 10 and the inner peripheral surface of the cylinder liner 40 are both sealing surfaces that constitute the sealed compression chamber. Friction between the cylinder 10 and the cylinder liner 40 can damage the sealing performance of the sealing surfaces.

[0149] Specifically, the cylinder 10 rotates circumferentially within the volume chamber 4001 of the cylinder liner 40. The cylinder 10 and the cylinder liner 40 form a friction pair. A textured structure 100 is formed on the contact surface between the cylinder 10 and the cylinder liner 40. The textured structure 100 reduces the contact area between the cylinder 10 and the cylinder liner 40. During the movement, oil in the gap between the surfaces of the friction pair enters the interior of the textured structure 100. During the relative movement between the cylinder 10 and the cylinder liner 40, the load-bearing capacity of the fluid film formed by the oil is enhanced, causing the surfaces of the two contact surfaces to tend to separate, reducing friction. The formed fluid film is more stable and tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between the cylinder 10 and the cylinder liner 40.

[0150] To address the issues of excessive friction in the pump body assembly of existing rotary cylinder compressors during operation, which leads to damage and compromises the pump body assembly's sealing performance, a textured structure can be installed between the cylinder 10 and the limiting plate to reduce friction and improve the sealing performance between them.

[0151] Specifically, such as Figures 6 to 33As shown, the pump body assembly includes a cylinder 10 and a limiting plate. The limiting plate is located on one side of the axial direction of the cylinder 10. The surface of the cylinder 10 that contacts the limiting plate is the first contact surface. The limiting plate has a second contact surface that cooperates with the first contact surface. The first contact surface and the second contact surface form a friction pair surface. A textured structure 100 is provided on the first contact surface and / or the second contact surface.

[0152] As can be seen from the above description, in the above embodiments of the present invention, by providing a textured structure 100 between the cylinder 10 and the limiting plate, the dynamic pressure effect in the textured structure 100 area is enhanced, increasing the lubrication performance between the cylinder 10 and the limiting plate, reducing the friction between the cylinder 10 and the limiting plate, and avoiding the problems of reduced component life and cylinder 10 tilting caused by wear between the cylinder 10 and the limiting plate. At the same time, providing the textured structure 100 can enhance the sealing between the cylinder 10 and the limiting plate, preventing gas leakage along the end face of the cylinder 10 and the end face of the limiting plate, thus avoiding the problem of cold loss.

[0153] Specifically, the limiting plate and the cylinder 10 rotate relative to each other. By creating a textured structure 100 on the contact surface between the limiting plate and the cylinder 10, the dynamic pressure effect of the textured area between the limiting plate and the cylinder 10 is enhanced during the movement of the cylinder 10 relative to the limiting plate. This increases the load-bearing capacity of the fluid film in the textured area, causing the surfaces of the two contact surfaces to tend to separate, reducing frictional power consumption, improving the lubrication performance of the limiting plate and the cylinder 10, promoting stable operation between the limiting plate and the cylinder 10, and increasing the service life of the limiting plate and the cylinder 10. Because a more stable fluid film is formed, it tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between the limiting plate and the cylinder 10.

[0154] like Figure 6 As shown, the cylinder 10 has a limiting protrusion ring 1011 along its axial direction, and the limiting plate has a limiting hole, with the limiting protrusion ring 1011 embedded in the limiting hole.

[0155] Specifically, during the rotation of the cylinder 10, the axial end face of the cylinder 10 and the end face of the limiting plate perpendicular to the cylinder 10 form a friction pair, while the outer ring surface of the limiting protrusion ring 1011 and the wall surface of the limiting hole form a friction pair.

[0156] Furthermore, the limiting plate includes an upper limiting plate 70 and a lower limiting plate 80 arranged along the axial direction of the cylinder 10. The upper limiting plate 70 is provided with an upper limiting hole 7001, and the lower limiting plate 80 is provided with a lower limiting hole 8001. Both end faces of the cylinder 10 in the axial direction are provided with limiting protrusions 1011. The upper limiting plate 70 and the lower limiting plate 80 are fixed, but the cylinder 10 rotates relative to them, thereby forming a friction pair between the cylinder 10 and the upper limiting plate 70 and the lower limiting plate 80.

[0157] It should be noted that, in Figures 7 to 33In specific embodiments, schemes for providing textured structures 100 on the cylinder 10 and the limiting plate are given respectively. In specific embodiments, textured structures 100 can be provided on both the cylinder 10 and the limiting plate at the same time, or textured structures 100 can be provided on only one of them. Since there are many combinations, not all combinations will be listed.

[0158] In this invention, the texture structure 100 is composed of a plurality of spaced-apart textured grooves. The texture structure 100 can be configured from spaced-apart, i.e., non-connected structures.

[0159] Specifically, when the textured structure 100 is composed of multiple spaced textured grooves, the angle between the centerline of the textured structure 100 and the rotation direction of the cylinder 10 is 10° to 60°. The centerline of the textured structure 100 is inclined relative to the rotation direction of the cylinder 10. During the rotation of the cylinder 10 relative to the limiting plate, this enhances the dynamic pressure effect between the cylinder 10 and the limiting plate, strengthens the fluid film's load-bearing capacity, increases the lubrication performance between the cylinder 10 and the limiting plate, reduces wear, and enhances sealing. It should be noted that when the groove opening of the textured groove is specifically defined as elliptical, the included angle α is the same as the aforementioned angle between the centerline of the textured structure 100 and the rotation direction of the cylinder 10; only the expression is different.

[0160] It should be noted that when the texture structure 100 is composed of multiple spaced texture grooves, the opening of the texture groove can be one or more of elliptical, circular, or polygonal shapes; the texture groove can also be spaced arc-shaped grooves with a preset deflection angle relative to the radial direction of the cylinder 10. Different views are given below to illustrate the different forms of the texture structure 100.

[0161] By providing different textured structures 100 on the cylinder 10 and the limiting plate, Figures 7 to 33 Multiple implementation methods. In Figures 7 to 24 In the specific embodiment shown, a textured structure is mainly provided on the limiting protrusion 1011 of the cylinder 10 or within the limiting hole of the limiting plate. Meanwhile... Figures 25 to 33 In the specific embodiment shown, a textured structure is mainly provided on the end face of the cylinder 10 or the surface of the flange structure facing the end face of the cylinder 10.

[0162] like Figures 7 to 9 In the specific embodiment shown, the texture structure 100 is formed on the limiting protrusion ring 1011 of the cylinder 10. When the texture structure 100 is composed of multiple texture grooves arranged at intervals, the groove opening of the texture groove is elliptical.

[0163] Specifically, the ratio between the minor axis *a* and the major axis *b* of the ellipse satisfies: 1.5 ≤ b / a ≤ 3.5. When the ratio between the major and minor axes of the ellipse is within the range of 1.5 to 3.5, the dynamic pressure effect of the textured area is enhanced during the relative movement of the cylinder 10 and the limiting plate. This strengthens the load-bearing capacity of the fluid film formed on the contact surface between the cylinder 10 and the limiting plate, improving the lubrication performance between them and reducing frictional losses.

[0164] like Figures 7 to 9 As shown, the range of the minor axis *a* of the ellipse is 0.008 mm ≤ *a* ≤ 0.05 mm, and the range of the major axis *b* is 0.016 mm ≤ *b* ≤ 0.1 mm. The major and minor axes of the ellipse are within these ranges, and the ratio 1.5 ≤ *b* / *a* ≤ 3.5 is maintained. When the values ​​of the minor and major axes are too large, the elliptical textured groove becomes too large, reducing the strength of the cylinder 10 and the limiting plate, thus affecting their service life. Furthermore, an excessively large elliptical textured groove will store excess oil, which is detrimental to the fluid film strength and causes oil waste. When the values ​​of the minor and major axes are too small, the amount of oil stored in the textured groove is insufficient, which is detrimental to enhancing the fluid film's load-bearing capacity. Conversely, an excessively small textured groove cannot store trace amounts of oil, which is detrimental to improving lubrication performance.

[0165] like Figures 7 to 9 As shown, the angle α between the major axis of the ellipse and the centerline of the cylinder 10 ranges from 10° to 60°. During the relative movement of the cylinder 10 with respect to the limiting plate, the inclined elliptical textured groove moves in the opposite direction to the fluid film. A value of 10° to 60° ensures a strong dynamic pressure effect during the relative movement of the cylinder 10 with respect to the limiting plate.

[0166] like Figures 10 to 12 In the specific embodiment shown, the texture structure 100 is formed on the limiting protrusion ring 1011 of the cylinder 10. When the texture structure 100 is composed of a plurality of texture grooves arranged at intervals, the opening of the texture groove is circular.

[0167] Specifically, when the textured structure 100 consists of multiple spaced textured grooves, the openings of the textured grooves are circular, and the radius of the textured grooves is between 0.01 mm and 0.08 mm. The size of the textured grooves should be controlled within the radius range of 0.01 mm to 0.08 mm. Too small or too large an equivalent diameter will affect the formation of the fluid film and its specific technical performance. Specifically, if the equivalent diameter is too small, the oil storage capacity inside the textured groove is low, which is not conducive to enhancing the fluid film's load-bearing capacity. If the equivalent diameter is too large, it leads to a reduction in the pump body's strength, service life, and safety.

[0168] like Figures 13 to 15In the specific embodiment shown, the texture structure 100 is formed on the wall of the upper limit hole 7001 of the upper limit plate 70, which is consistent with... Figures 7 to 9 The specific implementation shown is similar, with the groove opening of the textured groove being elliptical.

[0169] like Figures 16 to 18 In the specific embodiment shown, the texture structure 100 is formed on the wall of the upper limit hole 7001 of the upper limit plate 70, and... Figures 10 to 12 The specific implementation shown is similar, with the groove opening of the textured groove being circular.

[0170] like Figures 19 to 21 In the specific embodiment shown, the texture structure 100 is formed on the wall of the lower limiting hole 8001 of the lower limiting plate 80, and... Figures 7 to 9 The specific implementation shown is similar, with the groove opening of the textured groove being elliptical.

[0171] like Figures 22 to 24 In the specific embodiment shown, the texture structure 100 is formed on the wall of the lower limiting hole 8001 of the lower limiting plate 80, and... Figures 10 to 12 The specific implementation shown is similar, with the groove opening of the textured groove being circular.

[0172] like Figure 25 In the specific embodiment shown, the texture structure 100 is formed on the end face of the cylinder 10. When the texture structure 100 is composed of multiple texture grooves arranged at intervals, the texture grooves are arc-shaped grooves. Specifically, the arc-shaped grooves are spiral grooves with a preset angle.

[0173] Specifically, the textured grooves on the end face of cylinder 10 are spaced-apart arc-shaped grooves. The side of the arc-shaped groove facing the center of rotation is the low-pressure end, and the side of the arc-shaped groove away from the center of rotation is the high-pressure end. During the rotation of cylinder 10, the oil flows from the low-pressure end to the high-pressure end, which is the direction of fluid film movement, ω being the fluid film. The flow of oil from the low-pressure end to the high-pressure end during the rotation of cylinder 10 helps to strengthen the fluid film.

[0174] It should be noted that the deflection direction of the arc-shaped groove is the same as the rotation direction of the cylinder 10, that is, the deflection direction of the arc-shaped groove is opposite to the rotation direction of the fluid film.

[0175] like Figure 25 As shown, the spiral is a logarithmic spiral and satisfies:

[0176] Logarithmic spiral:

[0177] r = R2e θtanδ ,

[0178] In the formula, r and θ are the coordinates of the helical line point, R2 is the inner diameter of the helical groove, and δ is the helical angle;

[0179] Slot diameter ratio β:

[0180] β=(R1-R2) / (R0-R2),

[0181] In the formula, R1 is the outer diameter of the spiral groove, R0 is the outer diameter of cylinder 10, and R2 is the inner diameter of the spiral groove;

[0182] Slot width ratio γ:

[0183] γ=lw / lg

[0184] In the formula, lw is the width of the spiral groove, and lg is the width of the spiral groove;

[0185] The parameter ranges for helix angle, groove diameter ratio, and groove width ratio are as follows:

[0186] 10°≤δ≤30°, 0.25≤β≤0.65, 0.2≤γ≤0.7.

[0187] Specifically, by opening a logarithmic spiral textured structure 100 on the end face of the cylinder 10, the load-bearing capacity of the fluid film is enhanced, while the sealing performance is improved, reducing wear between the cylinder 10 and the limiting plate, and avoiding the problem of cylinder 10 tilting.

[0188] like Figure 25 As shown, the outer diameter R of cylinder 10 and the radius R1 of the area where the texture structure 100 is located satisfy the following condition: 0.4≤R1 / R≤0.6.

[0189] Specifically, the ratio of the radius of the textured structure 100 region to the outer diameter of the cylinder 10 ranges from 0.4 to 0.6, where the radius of the textured region is smaller than the radius of the outer diameter of the cylinder 10, which is R0. If the radius of the textured structure 100 region is too small, it is not conducive to forming a strong fluid film and cannot effectively reduce the friction between the cylinder 10 and the limiting plate; if the radius of the textured structure 100 region is too large, it will reduce the load-bearing capacity of the fluid film and affect the strength of the end face of the cylinder 10, thus reducing the service life of the cylinder 10.

[0190] like Figures 26 to 27 In the specific embodiment shown, the texture structure 100 is formed on the upper limit plate 70, and... Figure 20 The specific implementation shown is similar, with the textured groove being a spiral groove. The depth ha of the textured groove is from 0.002 mm to 0.08 mm.

[0191] like Figure 28 In the specific embodiment shown, the texture structure 100 is formed on the lower limit plate 80, and... Figure 20 The specific implementation shown is similar, with the textured groove being a spiral groove.

[0192] like Figure 29 In the specific embodiment shown, the texture structure 100 is formed on the end face of the upper limit plate 70. When the texture structure 100 is composed of a plurality of texture grooves arranged at intervals, the texture grooves are arc-shaped grooves. Specifically, the arc-shaped grooves are circular arc-shaped grooves with a preset angle.

[0193] like Figure 30 In the specific embodiment shown, the texture structure 100 is formed on the end face of the cylinder 10, and... Figure 24 The specific implementation shown is similar, with the textured groove being an arc-shaped groove.

[0194] Specifically, the circular arc groove and the spiral groove achieve similar technical effects. Both rotate to make the oil between the cylinder 10 and the limiting plate flow from the low pressure position to the high pressure position, thereby enhancing the carrying capacity of the fluid film, increasing the lubrication performance between the cylinder 10 and the limiting plate, and reducing the wear between the cylinder 10 and the limiting plate.

[0195] like Figure 31 In the specific embodiment shown, the texture structure 100 is formed on the end face of the upper limit plate 70. When the texture structure 100 is composed of multiple texture grooves arranged at intervals, the texture grooves are composed of straight grooves and micropores.

[0196] Specifically, the micropores are circular with a diameter ranging from 0.02 mm to 0.05 mm and a texture depth ranging from 0.002 mm to 0.08 mm. The micropores are set around the periphery of the straight groove and work in conjunction with the straight groove. During the rotation of the cylinder 10 relative to the limiting plate, the oil moves inside the straight groove. The oil inside the micropores helps to enhance the formation of the fluid film and improve the carrying capacity of the fluid film, thereby improving the lubrication performance between the cylinder 10 and the limiting plate and reducing the wear between the cylinder 10 and the limiting plate.

[0197] It should be noted that the micropores are provided in multiples and arranged in a circumferential array on the periphery of the straight groove away from the rotation center of the cylinder 10.

[0198] like Figures 32 to 33 In the specific embodiment shown, the texture structure 100 is formed on the end face of the cylinder 10, and... Figure 31 The specific implementation shown is similar, with the textured groove being formed by the combination of straight grooves and micropores.

[0199] In addition to the above-described embodiments, the texture structure 100, which is formed on the end face of the cylinder 10, can also be composed of multiple cross-arranged texture grooves, forming a mesh texture structure (not shown in the figure).

[0200] Specifically, the texture structure 100 consists of multiple intersecting texture grooves, which form a mesh texture structure.

[0201] When the texture structure 100 is composed of multiple intersecting texture grooves, each texture groove is one or more of straight grooves, curved grooves, and zigzag grooves. Specifically, when the texture structure 100 has an intersecting texture groove structure, the texture grooves are all of one type of straight groove, curved groove, and zigzag groove, or they can be a combination of straight grooves, curved grooves, and zigzag grooves.

[0202] Optionally, when the textured structure 100 consists of multiple intersecting textured grooves, the width of the textured grooves is between 0.02 mm and 0.16 mm. Specifically, if the width of the textured groove is too small, the oil storage capacity inside the textured groove is small, which is not conducive to enhancing the fluid film's carrying capacity. At the same time, textured grooves with too small a width cannot store trace amounts of wear debris and impurities brought by the oil. If the width of the textured groove is too large, it leads to a reduction in the strength of the pump body, as well as a reduction in service life and safety.

[0203] It should be noted that the arrangement of the texture structure 100 is not limited to the above situation. The arrangement of the texture structure 100 can also be other technical solutions that can achieve the technical effect of reducing friction and increasing sealing.

[0204] The friction pair clearance L between the first and second contact surfaces and the depth ha of the textured groove satisfy the following condition: ha / L is 0.4 to 0.8. Specifically, the friction pair clearance L is greater than the depth ha of the textured groove. If the friction pair clearance L is too small, the friction between the first and second contact surfaces will intensify; if the depth ha of the textured groove is too small, the lubrication of the first and second contact surfaces will decrease, making it difficult to retain lubricating oil. If the friction pair clearance L is too large, the fluid oil film's carrying capacity will decrease; if the depth ha of the textured groove is too large, it will affect the structural strength of the second contact surface and reduce the hydrodynamic lubrication effect. If the difference between the friction pair clearance L and the depth ha of the textured groove is too large, it will negatively affect the lubrication effect of the friction pair surface.

[0205] The area S of the friction pair surface and the total area S1 of the region where the textured structure 100 is located satisfy the following relationship: S1 / S is 5% to 40%. The total area of ​​the region where the textured structure 100 is located includes the area of ​​all textured structures 100. If the textured structure 100 is located in only one region, the total area is the total area of ​​the textured structures 100 in that region. If the textured structure 100 is located in multiple regions, the total area is the sum of the areas of textured structures 100 in all regions. If the proportion of the total area S1 of the region where the textured structure 100 is located is too large, it will affect the overall structural strength of the limiting plate or cylinder 10. Simultaneously, if the textured holes are too small, the effect of reducing friction will not be achieved. If the proportion of the total area S1 of the region where the textured structure 100 is located is too small, it will increase friction and wear under load conditions, and also increase the gap size, affecting sealing performance.

[0206] The pump assembly of the present invention also includes a cylinder liner 40, a piston 20 and a rotating shaft 30. The cylinder 10 is rotatably disposed in the cylinder liner 40. A piston hole 106 is provided on the cylinder 10 along its radial direction. The piston 20 is slidably disposed in the piston hole 106. The rotating shaft 30 passes through the piston 20 and drives the piston 20 to reciprocate along the extension direction of the piston hole 106. The cylinder 10 rotates to drive the piston 20 to rotate. The limiting plate is located at the axial end of the cylinder 10.

[0207] Specifically, the cylinder liner 40, cylinder 10, limiting plate, piston 20 and rotating shaft 30 work together to form a pump body assembly. By opening a textured structure 100 between the cylinder 10 and the limiting plate, the wear between the cylinder 10 and the limiting plate is reduced, and the phenomenon that the cylinder 10 tilting affects the piston 20 and rotating shaft 30 is avoided.

[0208] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects:

[0209] In the above embodiments of the present invention, by creating a textured structure 100 between the cylinder 10 and the limiting plate, the dynamic pressure effect of the textured structure 100 region is enhanced, increasing the lubrication performance between the cylinder 10 and the limiting plate, reducing the friction between the cylinder 10 and the limiting plate, and avoiding the problems of reduced component life and cylinder 10 tilting caused by wear between the cylinder 10 and the limiting plate. Simultaneously, the textured structure 100 enhances the sealing performance between the cylinder 10 and the limiting plate, preventing gas leakage along the end face of the cylinder 10 and the end face of the limiting plate, thus avoiding the problem of cold loss.

[0210] Specifically, the limiting plate and the cylinder 10 rotate relative to each other. By creating a textured structure 100 on the contact surface between the limiting plate and the cylinder 10, the dynamic pressure effect of the textured area between the limiting plate and the cylinder 10 is enhanced during the movement of the cylinder 10 relative to the limiting plate. This increases the load-bearing capacity of the fluid film in the textured area, causing the surfaces of the two contact surfaces to tend to separate, reducing frictional power consumption, improving the lubrication performance of the limiting plate and the cylinder 10, promoting stable operation between the limiting plate and the cylinder 10, and increasing the service life of the limiting plate and the cylinder 10. Because a more stable fluid film is formed, it tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between the limiting plate and the cylinder 10.

[0211] To address the issues of excessive friction in the pump body assembly of existing rotary cylinder compressors during operation, which leads to damage to the pump body assembly and compromises its sealing performance, a textured structure 100 can be provided on the contact surface between the cylinder 10 and the piston 20 to reduce the friction between them and improve their sealing performance.

[0212] Specifically, such as Figures 34 to 43 As shown, the pump body assembly includes a cylinder liner 40, a cylinder 10, and a piston 20. The cylinder 10 is rotatably disposed within the cylinder liner 40, and a piston hole 106 is provided on the cylinder 10 along its radial direction. The piston 20 is slidably disposed within the piston hole 106 and reciprocates along the extension direction of the piston hole 106. The cylinder 10 rotates to drive the piston 20 to rotate. The surface of the piston hole 106 is a first contact surface, and the piston 20 has a second contact surface that mates with the first contact surface. The first contact surface and the second contact surface form a friction pair surface, and a textured structure 100 is provided on the first contact surface and / or the second contact surface.

[0213] As can be seen from the above description, in the above embodiments of the present invention, by providing a textured structure 100 on the contact surface of the cylinder 10 and the piston 20, the textured structure 100 can reduce the frictional force between the cylinder 10 and the piston 20, lower the frictional temperature between the piston 20 and the cylinder 10, and avoid deformation of parts due to excessive temperature. This can prevent refrigerant leakage caused by uneven contact surfaces between the piston 20 and the cylinder 10. Currently, existing pump bodies have many friction pairs and require high fluid lubrication. During operation, the piston 20 and cylinder 10 of the current pump body undergo slight deformation due to heat and force, increasing the frictional force between the contact surfaces and causing wear. The slight deformation of the parts leads to unevenness on the outer surface of the parts, which can cause refrigerant leakage due to uneven gaps.

[0214] Specifically, piston 20 reciprocates within piston bore 106 of cylinder 10 along the extension direction of piston bore 106. Cylinder 10 and piston 20 form a friction pair. A textured structure 100 is formed on the contact surface of cylinder 10 and piston 20. The textured structure 100 reduces the contact area between cylinder 10 and piston 20. During movement, oil in the gap between the surfaces of the friction pair enters the interior of the textured structure 100. Simultaneously, during the relative movement of piston 20 and cylinder 10, the load-bearing capacity of the fluid film formed by the oil is enhanced, causing the surfaces of the two contact surfaces to tend to separate, reducing friction. Due to the formation of a more stable fluid film, the fluid film tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between piston 20 and cylinder 10. The textured structure 100 has the function of storing oil and can also store trace amounts of wear debris and impurities brought by the oil, promoting stable operation between piston 20 and cylinder 10 and increasing the service life of piston 20 and cylinder 10.

[0215] It should be noted that, in Figures 36 to 43 In the specific embodiment shown, both the piston 20 and the cylinder 10 are provided with a textured structure 100. However, in actual products, the textured structure 100 may be provided on only one of them. Since the above-mentioned effect can be achieved by providing the textured structure 100 on only one of them, no further specific embodiments are given here.

[0216] like Figure 36 and Figure 39 As shown, the texture structure 100 consists of multiple spaced-apart textured grooves. Specifically, the texture structure 100 can be composed of spaced-apart, non-connected structures.

[0217] like Figures 36 to 43 As shown, when the texture structure 100 is composed of multiple spaced texture grooves, the openings of the texture grooves are elliptical, circular, or polygonal, or one or more of these shapes. Specifically, the polygon is rhomboid.

[0218] Specifically, the grooves of the textured grooves can be elliptical, circular, or polygonal, and can be distributed at intervals. Alternatively, textured grooves with various different shapes of grooves can be distributed at intervals.

[0219] like Figure 36 and Figure 39As shown, when the groove opening of the textured groove is circular, the equivalent diameter of the textured groove is 0.02mm to 0.5mm. The size of the textured groove should be controlled within the range of 0.02mm to 0.5mm. An equivalent diameter that is too small or too large will affect the formation of the fluid film and its specific technical performance. Specifically, if the equivalent diameter is too small, the oil storage capacity inside the textured groove is low, which is not conducive to enhancing the fluid film's load-bearing capacity. At the same time, a textured groove that is too small cannot store trace amounts of wear debris and impurities brought by the oil. If the equivalent diameter is too large, it leads to a reduction in the pump body's strength, service life, and safety.

[0220] In a specific embodiment not shown, the arrangement of the texture structure 100 is similar to... Figures 36 to 43 The methods given are different.

[0221] Specifically, the texture structure 100 consists of multiple intersecting texture grooves, which form a mesh texture structure.

[0222] When the texture structure 100 is composed of multiple intersecting texture grooves, each texture groove is one or more of straight grooves, curved grooves, and zigzag grooves. Specifically, when the texture structure 100 has an intersecting texture groove structure, the texture grooves are all of one type of straight groove, curved groove, and zigzag groove, or they can be a combination of straight grooves, curved grooves, and zigzag grooves.

[0223] Optionally, when the textured structure 100 consists of multiple intersecting textured grooves, the width of the textured grooves is between 0.02 mm and 0.5 mm. Specifically, if the width of the textured groove is too small, the oil storage capacity inside the textured groove is small, which is not conducive to enhancing the fluid film's load-bearing capacity. At the same time, textured grooves with too small a width cannot store trace amounts of wear debris and impurities brought by the oil. If the width of the textured groove is too large, it leads to a reduction in the strength of the pump body, as well as a reduction in service life and safety.

[0224] It should be noted that the arrangement of the texture structure 100 is not limited to the above situation. The arrangement of the texture structure 100 can also be other technical solutions that can achieve the technical effect of reducing friction and increasing sealing.

[0225] like Figure 36 and Figure 43As shown, the friction pair clearance L between the first and second contact surfaces and the depth H of the textured groove satisfy the following relationship: H / L is 0.4 to 0.8. Specifically, the friction pair clearance L is greater than the depth H of the textured groove. If the friction pair clearance L is too small, the friction between the first and second contact surfaces will intensify; if the depth H of the textured groove is too small, the lubrication of the first and second contact surfaces will decrease, making it difficult to store lubricating oil. If the friction pair clearance L is too large, the fluid oil film's carrying capacity will decrease; if the depth H of the textured groove is too large, it will affect the structural strength of the second contact surface and reduce the hydrodynamic lubrication effect. If the difference between the friction pair clearance L and the depth H of the textured groove is too large, it will negatively affect the lubrication effect of the friction pair surface.

[0226] like Figure 36 and Figure 43 As shown, the area S of the friction pair surface and the total area S1 of the region where the texture structure 100 is located satisfy the following relationship: S1 / S is 5% to 10%. The total area of ​​the region where the texture structure 100 is located includes the area of ​​all texture structures 100. If the texture structure 100 is located in only one region, the total area is the total area of ​​the texture structures 100 in that region. If the texture structure 100 is located in multiple regions, the total area is the sum of the areas of texture structures 100 in all regions. If the proportion of the total area S1 of the region where the texture structure 100 is located is too large, it will affect the overall structural strength of the piston 20 or cylinder 10. Simultaneously, if the texture hole is too small, it will not achieve the effect of reducing friction. If the proportion of the total area S1 of the region where the texture structure 100 is located is too small, it will increase friction and wear under load conditions, and also increase the clearance size, affecting sealing performance.

[0227] like Figure 36 and Figure 43 As shown, when the texture structure 100 is composed of multiple spaced textured grooves and the openings of the textured grooves are elliptical, the angle between the centerline of the texture structure 100 and the relative sliding direction of the shaft is 60° to 90°. Adjusting the angle between the centerline of the texture structure 100 and the relative sliding direction of the shaft can increase the hydrodynamic lubrication effect and enhance sealing performance.

[0228] It should be noted that the axis-to-axis sliding direction here refers to the sliding direction of the rotating shaft 30 relative to the piston 20. Since in actual operation, the rotating shaft 30 only rotates, while the piston 20 slides relative to the rotating shaft 30 while rotating, the axis-to-axis sliding direction can also be understood as the extension direction of the sliding hole of the piston 20. Specifically, during installation, the rotating shaft 30 passes through the sliding hole. When the rotating shaft 30 rotates, it appears to slide back and forth within the sliding hole, but this is not actually to restrict the rotating shaft 30 from sliding itself. Furthermore, the centerline of the texture structure 100 refers to the direction of the major axis of the ellipse in the figure. Additionally, the angle between the centerline of the texture structure 100 and the axis-to-axis sliding direction is actually similar to the angle α in other embodiments, and will not be elaborated here.

[0229] The texture structure 100 in this invention includes a piston texture structure 205 and a cylinder texture structure 105. At least a portion of the second contact surface of the piston 20 is provided with the piston texture structure 205, and at least a portion of the first contact surface of the cylinder 10 is provided with the cylinder texture structure 105. The piston texture structure 205 and the cylinder texture structure 105 are correspondingly arranged.

[0230] Specifically, piston textured structures 205 are formed on both the second contact surface of piston 20 and the first contact surface of cylinder 10, increasing the area of ​​textured structures 100. During the relative sliding process between piston 20 and cylinder 10, piston textured structures 205 and cylinder textured structures 105 are formed on the surfaces of piston 20 and cylinder 10, effectively reducing the frictional force during the sliding process between piston 20 and cylinder 10, and reducing the working wear of piston 20 and cylinder 10.

[0231] In addition to the aforementioned specific embodiment in which piston texture structure 205 is provided on all the first contact surfaces, piston texture structure 205 is provided on a portion of the first contact surface of piston 20, and cylinder texture structure 105 is provided on a portion of the second contact surface of cylinder 10. Providing piston texture structure 205 and cylinder texture structure 105 on a portion of the first contact surface can reduce the processing process and also reduce the friction between piston 20 and cylinder 10. During the movement of cylinder 10 and piston 20, it can play a role in lubrication and anti-wear, and reduce wear.

[0232] like Figures 34 to 43In a specific implementation, the pump body assembly of the present invention further includes a rotating shaft 30, at least a portion of which passes through the piston 20 and drives the piston 20 to move. At least one end of the rotating shaft 30 extends outward from the cylinder liner 40. The second contact surface includes a first region surface 201, a second region surface 202, a third region surface 203, and a fourth region surface 204 connected in sequence. The first region surface 201 and the third region surface 203 are arranged opposite to each other and perpendicular to the rotating shaft 30. At least one of the first region surface 201, the second region surface 202, the third region surface 203, and the fourth region surface 204 is provided with a textured structure 100.

[0233] Specifically, the second contact surface is formed by the cooperation of the first region surface 201, the second region surface 202, the third region surface 203 and the fourth region surface 204, and at least one of the first region surface 201, the second region surface 202, the third region surface 203 and the fourth region surface 204 is provided with a texture structure 100. The size of the texture structure 100 on different regions of the first region surface 201, the second region surface 202, the third region surface 203 and the fourth region surface 204 can be the same or different.

[0234] like Figures 34 to 43 In a specific implementation, the first contact surface includes a fifth region surface 101, a sixth region surface 102, a seventh region surface 103, and an eighth region surface 104 connected in sequence. The fifth region surface 101 and the seventh region surface 103 are arranged opposite to each other and perpendicular to the rotation axis 30. At least one of the fifth region surface 101, the sixth region surface 102, the seventh region surface 103, and the eighth region surface 104 is provided with a textured structure 100.

[0235] Specifically, the first contact surface includes a fifth region surface 101, a sixth region surface 102, a seventh region surface 103, and an eighth region surface 104 connected in sequence. At least one of the fifth region surface 101, the sixth region surface 102, the seventh region surface 103, and the eighth region surface 104 is provided with a texture structure 100. The size of the texture structure 100 on different regions of the fifth region surface 101, the sixth region surface 102, the seventh region surface 103, and the eighth region surface 104 can be the same or different.

[0236] exist Figure 36 and Figure 37In the specific embodiment shown, the second contact surfaces of the piston 20, namely the first region surface 201, the second region surface 202, the third region surface 203 and the fourth region surface 204, are all provided with piston texture structures 205. The first contact surfaces of the cylinder 10, namely the fifth region surface 101, the sixth region surface 102, the seventh region surface 103 and the eighth region surface 104, are all provided with cylinder texture structures 105. The piston texture structure 205 and the cylinder texture structure 105 cooperate to form a full texture structure 100, and the piston texture structure 205 and the cylinder texture structure 105 are correspondingly arranged. During the reciprocating motion of piston 20 within cylinder 10 along the extension direction of piston bore 106, the total area of ​​the full textured structure 100 is the largest. Therefore, the fluid oil film formed between piston textured structure 205 and cylinder textured structure 105 has the strongest load-bearing capacity, which minimizes the frictional force between cylinder 10 and piston 20 during relative motion. At this time, textured structure 100 can store more oil to ensure the sealing between cylinder 10 and piston 20, promote stable operation between piston 20 and cylinder 10, and increase the service life of piston 20 and cylinder 10.

[0237] exist Figure 40 and Figure 41 In the specific embodiment shown, piston textured structures 205 are formed on the first region surface 201 and the third region surface 203 of the second contact surface of the piston 20, and cylinder textured structures 105 are formed on the fifth region surface 101 and the seventh region surface 103 of the first contact surface of the cylinder 10. The piston textured structures 205 and cylinder textured structures 105 are correspondingly arranged. During the relative movement between the cylinder 10 and the piston 20, the bearing capacity of the fluid oil film formed between the cylinder textured structure 105 and the piston textured structure 205 is enhanced, reducing the friction between the first region surface 201 and the fifth region surface 101, and also reducing the friction between the third region surface 203 and the seventh region surface 103, thereby reducing wear between the cylinder 10 and the piston 20. It should be noted that forming textured structures 100 in part of the first and second contact surfaces helps to reduce processing steps and lower processing costs.

[0238] exist Figure 42 and Figure 43In the specific embodiment shown, piston textured structures 205 are formed on the second region surface 202 and the fourth region surface 204 of the second contact surface of the piston 20, and cylinder textured structures 105 are formed on the sixth region surface 102 and the eighth region surface 104 of the first contact surface of the cylinder 10. The piston textured structures 205 and cylinder textured structures 105 are correspondingly arranged. During the relative movement between the cylinder 10 and the piston 20, the bearing capacity of the fluid oil film formed between the cylinder textured structure 105 and the piston textured structure 205 is enhanced, reducing the friction between the second region surface 202 and the sixth region surface 102, and simultaneously reducing the friction between the fourth region surface 204 and the eighth region surface 104, thereby reducing wear between the cylinder 10 and the piston 20. It should be noted that forming textured structures 100 in parts of the first and second contact surfaces helps to reduce processing steps and lower processing costs.

[0239] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects:

[0240] In the above embodiments of the present invention, by providing a textured structure 100 on the contact surface of the cylinder 10 and the piston 20, the textured structure 100 can reduce the frictional force between the cylinder 10 and the piston 20, lower the frictional temperature between the piston 20 and the cylinder 10, and prevent deformation of parts due to excessive temperature. This also avoids the problem of refrigerant leakage caused by uneven contact surfaces between the piston 20 and the cylinder 10. Currently, existing pump bodies have many friction pairs and require high fluid lubrication. During operation, the piston 20 and cylinder 10 of the current pump body undergo slight deformation due to heat and force, increasing the frictional force between the contact surfaces and causing wear. The slight deformation of the parts leads to unevenness on the outer surface of the parts, which can cause refrigerant leakage due to uneven gaps.

[0241] Specifically, piston 20 reciprocates within piston bore 106 of cylinder 10 along the extension direction of piston bore 106. Cylinder 10 and piston 20 form a friction pair. A textured structure 100 is formed on the contact surface of cylinder 10 and / or piston 20. The textured structure 100 reduces the contact area between cylinder 10 and piston 20. During movement, oil in the gap between the surfaces of the friction pair enters the interior of the textured structure 100. Simultaneously, during the relative movement of piston 20 and cylinder 10, the load-bearing capacity of the fluid film formed by the oil is enhanced, causing the surfaces of the two contact surfaces to tend to separate, reducing friction. Due to the formation of a more stable fluid film, the fluid film tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between piston 20 and cylinder 10. The textured structure 100 has the function of storing oil and can also store trace amounts of wear debris and impurities brought by the oil, promoting stable operation between piston 20 and cylinder 10 and increasing the service life of piston 20 and cylinder 10.

[0242] To address the issues of excessive friction in the pump body assembly of existing rotary cylinder compressors during operation, which leads to damage and compromises the pump body assembly's sealing performance, a textured structure 100 can be provided on the contact surface between the piston 20 and the rotating shaft 30 to reduce friction between them and improve their sealing performance.

[0243] Specifically, such as Figures 44 to 57 As shown, the pump body assembly includes a rotating shaft 30 and a piston 20. The piston 20 has a sliding hole, and the sliding hole has at least one set of opposing sliding hole walls. The sliding hole walls are planar and serve as a first contact surface 2001. At least a portion of the rotating shaft 30 passes through the sliding hole and has a sliding mating surface that slides in contact with the sliding hole wall. The sliding mating surface is a second contact surface 3001. The first contact surface 2001 and the second contact surface 3001 form a friction pair surface. A textured structure 100 is provided on the first contact surface 2001 and / or the second contact surface 3001.

[0244] As can be seen from the above description, by setting a textured structure 100 on the contact surface of the shaft 30 and the piston 20, the dynamic pressure effect in the textured structure 100 area is enhanced, thereby improving the lubrication performance between the shaft 30 and the piston 20 and avoiding problems such as wear and non-adhesion between the shaft and the piston 20. Currently, the shaft 30 of the existing pump body provides the power source for the pump body. The shaft 30 transmits the torque output by the motor to the piston 20 to achieve refrigerant compression. During the rotation of the shaft 30, friction will occur between it and the piston 20. Especially when the pump body assembly is running at high frequency under heavy working conditions, the friction between the shaft 30 and the piston 20 will be intensified, and problems such as wear and unreliable adhesion will occur between the shaft 30 and the piston 20.

[0245] Specifically, the rotating shaft 30 passes through a sliding hole on the piston 20. During the rotation of the rotating shaft 30, the piston 20 rotates with the cylinder 10 while simultaneously reciprocating relative to the rotating shaft 30 in a direction perpendicular to the rotating shaft 30. The rotating shaft 30 and piston 20 cooperate to form a friction pair. By creating a textured structure 100 on the contact surface of the rotating shaft 30 and / or piston 20, the textured structure 100 reduces the contact area between the rotating shaft 30 and piston 20. During the movement of the piston 20 relative to the rotating shaft 30, the dynamic pressure effect of the textured area is enhanced, improving the load-bearing capacity of the fluid film. The fluid film becomes more stable, causing the surfaces of the two contact surfaces to tend to separate, reducing frictional power consumption, and improving the lubrication performance between the rotating shaft 30 and piston 20. Because a more stable fluid film is formed, it tightly adheres to the surfaces of the two contact surfaces, improving the sealing between the rotating shaft 30 and piston 20, promoting stable operation between the piston 20 and rotating shaft 30, and increasing the service life of the piston 20 and rotating shaft 30.

[0246] It should be noted that the reference Figure 47As shown, the direction of fluid membrane movement is U. The inclination direction of the center line of the texture structure 100 is opposite to the direction of fluid membrane movement, which is beneficial to enhance the dynamic pressure effect of the texture area, improve the load-bearing capacity of the fluid membrane, reduce the friction between the rotating shaft 30 and the piston 20, and reduce friction loss.

[0247] It should be noted that, in Figures 46 to 57 The specific embodiments shown illustrate schemes where the textured structure 100 is provided on the piston 20 and the rotating shaft 30, respectively. In specific embodiments, the textured structure 100 can be provided on both the piston 20 and the rotating shaft 30 simultaneously, or it can be provided on only one of them. Since there are many combinations, they will not be listed one by one. Different figures will be provided below to illustrate different forms of the textured structure 100.

[0248] like Figures 46 to 57 As shown, the texture structure 100 consists of multiple spaced-apart textured grooves. Specifically, the texture structure 100 can be composed of spaced-apart, non-connected structures.

[0249] It should be noted that when the texture structure 100 is composed of multiple texture grooves arranged at intervals, the groove openings of the texture grooves are one or more of the following shapes: elliptical, circular, and polygonal.

[0250] Specifically, the polygon is a rhombus.

[0251] Below, based on the different texture structures 100 opened on the rotating shaft 30 or the piston 20, the following are provided: Figures 46 to 57 Multiple implementation methods.

[0252] exist Figure 46 and Figure 47 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30. When the texture structure 100 is composed of a plurality of spaced texture grooves, the opening of the texture grooves is elliptical.

[0253] Specifically, the ratio between the minor axis 'a' and the major axis 'b' of the ellipse satisfies: 1.5 ≤ b / a ≤ 3.5. When the ratio between the major and minor axes of the ellipse is within the range of 1.5 to 3.5, the dynamic pressure effect of the textured region is enhanced during the relative movement of the shaft 30 and the piston 20. The load-bearing capacity of the fluid film formed on the contact surface between the shaft 30 and the piston 20 is strengthened, thereby improving the lubrication performance between the shaft 30 and the piston 20 and reducing frictional loss.

[0254] like Figures 46 to 47As shown, the range of the minor axis *a* of the ellipse is 0.008 mm ≤ *a* ≤ 0.05 mm, and the range of the major axis *b* is 0.016 mm ≤ *b* ≤ 0.1 mm. The major and minor axes of the ellipse are within these ranges, and 1.5 ≤ *b* / *a* ≤ 3.5 is maintained. When the values ​​of the minor and major axes are too large, the strength of the rotating shaft 30 and piston 20 decreases due to the excessively large elliptical textured groove, affecting their service life. Furthermore, an excessively large elliptical textured groove will store excess oil, which is detrimental to fluid film strength and causes oil waste. When the values ​​of the minor and major axes are too small, the amount of oil stored in the textured groove is insufficient, which is detrimental to enhancing the fluid film's load-bearing capacity. Conversely, an excessively small textured groove cannot store trace amounts of oil, which is detrimental to improving lubrication performance.

[0255] like Figures 46 to 47 As shown, the angle α between the axis of the major axis of the ellipse and the center line of the rotating shaft 30 ranges from 10° to 60°. During the relative motion of the rotating shaft 30 with respect to the piston 20, the inclined elliptical textured groove moves in the opposite direction to the fluid film. When the value of α is within the range of 10° to 60°, a strong dynamic pressure effect is ensured during the relative motion of the rotating shaft 30 with respect to the piston 20.

[0256] like Figures 46 to 47 As shown, along the axial direction of the rotation axis 30, the distance between the minor axes of two adjacent ellipses is q; along the circumferential direction of the rotation axis 30, the distance between the major axes of two adjacent ellipses is p; where q and p satisfy: 1.5≤q / p≤3.

[0257] Specifically, the distance between the two elliptical grooves is controlled by adjusting the distance between the minor axes and the major axes of two adjacent elliptical grooves. When two adjacent elliptical grooves are too close, the excessive number of elliptical grooves reduces the strength of the shaft 30 and piston 20, affecting their service life. When two adjacent elliptical grooves are too far apart, it is not conducive to strengthening the fluid film and reducing the friction between the shaft 30 and piston 20. It should be noted that when the values ​​of q and p are appropriate and satisfy 1.5≤q / p≤3, it is beneficial to strengthen the load-bearing capacity of the fluid film without affecting the strength of the shaft 30 and piston 20.

[0258] It should be noted that the relationships between q and p, and between a and b, should satisfy: b and q satisfy 5b ≤ q ≤ 15b, and a and p satisfy 5a ≤ p ≤ 15a. By limiting the major axis and minor axis of the ellipse and the circumferential spacing, the texture structure 100 can achieve the best technical effect, that is, the fluid film between the rotating shaft 30 and the piston 20 has the strongest load-bearing capacity, effectively improving the lubrication performance between the rotating shaft 30 and the piston 20.

[0259] exist Figure 48 and Figure 49 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30. When the texture structure 100 is composed of a plurality of spaced texture grooves, the openings of the texture grooves are circular.

[0260] When the textured structure 100 consists of multiple spaced textured grooves, the openings of the textured grooves are circular, and the equivalent diameter of the textured grooves is 0.008 mm to 0.05 mm. The size of the textured grooves should be controlled within the range of 0.008 mm to 0.05 mm of equivalent diameter. An equivalent diameter that is too small or too large will affect the formation of the fluid film and its specific technical performance. Specifically, if the equivalent diameter is too small, the oil storage capacity inside the textured groove is small, which is not conducive to enhancing the fluid film's load-bearing capacity. At the same time, a textured groove that is too small cannot store trace amounts of wear debris and impurities brought by the oil. If the equivalent diameter is too large, it leads to a reduction in the pump body's strength, service life, and safety.

[0261] exist Figure 50 and Figure 51 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30. When the texture structure 100 is composed of multiple spaced texture grooves, the openings of the texture grooves are polygonal. Among them, the one shown in the figure is rhomboid.

[0262] Figures 52 to 54 In the specific embodiment shown, the texture structure 100 is formed on the piston 20. (And...) Figure 46 and Figure 47 The specific implementation shown is similar, and the groove of the texture structure 100 is elliptical.

[0263] Figure 55 and Figure 57 In the specific embodiment shown, the texture structure 100 is formed on the piston 20. (And...) Figure 48 and Figure 49 The specific implementation shown is similar, and the groove of the texture structure 100 is circular.

[0264] In addition to the above-described embodiments, the texture structure 100 may also consist of multiple intersecting texture grooves, which together form a mesh texture structure (not shown in the figure).

[0265] When the texture structure 100 is composed of multiple intersecting texture grooves, each texture groove is one or more of straight grooves, curved grooves, and zigzag grooves. Specifically, when the texture structure 100 has an intersecting texture groove structure, the texture grooves are all of one type of straight groove, curved groove, and zigzag groove, or they can be a combination of straight grooves, curved grooves, and zigzag grooves.

[0266] Optionally, when the textured structure 100 consists of multiple intersecting textured grooves, the width of the textured grooves is between 0.008 mm and 0.05 mm. Specifically, if the width of the textured groove is too small, the oil storage capacity inside the textured groove is small, which is not conducive to enhancing the fluid film's carrying capacity. At the same time, textured grooves with too small a width cannot store trace amounts of wear debris and impurities brought by the oil. If the width of the textured groove is too large, it leads to a reduction in the strength of the pump body, as well as a reduction in service life and safety.

[0267] It should be noted that the arrangement of the texture structure 100 is not limited to the above situation. The arrangement of the texture structure 100 can also be other technical solutions that can achieve the technical effect of reducing friction and increasing sealing.

[0268] like Figure 46 and Figure 57 As shown, the friction pair clearance L between the first contact surface 2001 and the second contact surface 3001 satisfies the following relationship with the depth H of the textured groove: H / L is 0.4 to 0.8. Specifically, the friction pair clearance L is greater than the depth H of the textured groove. If the friction pair clearance L is too small, the friction between the first contact surface 2001 and the second contact surface 3001 will intensify; if the depth H of the textured groove is too small, the lubrication of the first contact surface 2001 and the second contact surface 3001 will decrease, making it difficult to store lubricating oil. If the friction pair clearance L is too large, the fluid oil film carrying capacity will decrease; if the depth H of the textured groove is too large, it will affect the structural strength of the second contact surface 3001 and reduce the hydrodynamic lubrication effect. If the difference between the friction pair clearance L and the depth H of the textured groove is too large, it will negatively affect the lubrication effect of the friction pair surface.

[0269] like Figure 46 and Figure 57 As shown, the area S of the friction pair surface and the total area S1 of the region where the texture structure 100 is located satisfy the following relationship: S1 / S is 5% to 40%. The total area of ​​the region where the texture structure 100 is located includes the area of ​​all texture structures 100. If the texture structure 100 is located in only one region, the total area is the total area of ​​the texture structures 100 in that region. If the texture structure 100 is located in multiple regions, the total area is the sum of the areas of texture structures 100 in all regions. If the proportion of the total area S1 of the region where the texture structure 100 is located is too large, it will affect the piston 20 or the overall structural strength of the piston 20. Simultaneously, if the texture hole is too small, it will not achieve the effect of reducing friction. If the proportion of the total area S1 of the region where the texture structure 100 is located is too small, it will increase friction and wear under load conditions, and also increase the clearance size, affecting sealing performance.

[0270] exist Figures 46 to 51In the specific embodiment shown, a textured structure 100 is formed on the second contact surface 3001 of the rotating shaft 30. During the reciprocating motion of the piston 20 relative to the rotating shaft 30 along the vertical direction of the rotating shaft 30, the textured structure 100 on the rotating shaft 30 enhances the load-bearing capacity of the fluid oil film formed between the rotating shaft 30 and the piston 20, reducing the frictional force during the relative motion of the rotating shaft 30 and the piston 20. At this time, the fluid film formed by the textured structure 100 can improve the sealing performance between the rotating shaft 30 and the piston 20, promote the stable operation between the piston 20 and the rotating shaft 30, and reduce the frictional loss between the piston 20 and the rotating shaft 30. At the same time, forming the textured structure 100 only on the second contact surface 3001 of the rotating shaft 30 is beneficial to reduce the processing process and lower the processing cost.

[0271] exist Figures 52 to 57 In the specific embodiment shown, a textured structure 100 is formed on the first contact surface 2001 of the piston 20. During the reciprocating motion of the piston 20 relative to the rotating shaft 30 in the vertical direction of the rotating shaft 30, the textured structure 100 on the piston 20 enhances the load-bearing capacity of the fluid oil film formed between the rotating shaft 30 and the piston 20, reducing the frictional force in the relative motion between the rotating shaft 30 and the piston 20. At this time, the fluid film formed by the textured structure 100 can improve the sealing between the rotating shaft 30 and the piston 20, promote the stable operation between the piston 20 and the rotating shaft 30, and reduce the frictional loss between the piston 20 and the rotating shaft 30. At the same time, the textured structure 100 is only formed on the second contact surface 3001 of the rotating shaft 30, which helps to reduce the processing process and reduce the processing cost.

[0272] like Figure 44 As shown, the pump body assembly of the present invention also includes a cylinder liner 40, a cylinder 10 rotatably disposed inside the cylinder liner 40, a piston hole is provided on the cylinder 10 along its radial direction, a piston 20 is slidably disposed in the piston hole, a rotating shaft 30 passes through the piston 20 and drives the piston 20 to reciprocate along the extension direction of the piston hole, and the cylinder 10 and the piston 20 rotate synchronously.

[0273] Specifically, during operation, the cylinder 10 rotates within the cylinder liner 40, and the piston 20 rotates with the cylinder 10. The piston 20 reciprocates along the extension direction of the piston hole, that is, the piston 20 reciprocates along the direction perpendicular to the rotating shaft 30. The rotating shaft 30 provides power to the pump assembly during rotation. The rotating shaft 30 transmits the torque output by the motor to the piston 20 to achieve refrigerant compression. The cylinder liner 40, cylinder 10, piston 20 and flange structure cooperate to form the pump assembly. A textured structure 100 is provided on the rotating shaft 30 and piston 20 to reduce frictional loss between the rotating shaft 30 and piston 20.

[0274] To address the issues of excessive friction in the pump body assembly of existing rotary cylinder compressors during operation, which leads to damage and compromises the pump body assembly's sealing performance, a textured structure 100 can be provided on the contact surface between the rotating shaft 30 and the flange structure. This reduces the friction between the rotating shaft 30 and the flange structure while simultaneously enhancing their sealing performance.

[0275] Specifically, such as Figures 58 to 86 As shown, the pump body assembly includes a rotating shaft 30 and a flange structure. The flange structure has a flange hole through which the rotating shaft 30 passes. The flange hole has a first contact surface, and the portion of the rotating shaft 30 located inside the flange hole has a second contact surface. The first contact surface and the second contact surface form a friction pair surface. A textured structure 100 is provided on the first contact surface and / or the second contact surface.

[0276] As can be seen from the above description, by setting a textured structure 100 on the contact surface between the shaft 30 and the flange structure, the dynamic pressure effect in the textured structure 100 area is enhanced, thereby improving the lubrication performance between the shaft 30 and the flange structure and avoiding problems such as shaft 30 wear, shaft 30 breakage, and flange structure wear. Currently, the existing pump body's shaft 30 provides the power source for the pump body, and the flange structure supports the shaft 30. During operation, the shaft 30 will generate friction with the flange structure. Especially when the pump body assembly operates under heavy-duty, high-frequency conditions, the friction between the shaft 30 and the flange structure will intensify, leading to problems such as shaft 30 wear, breakage, and flange shaft hole wear.

[0277] Specifically, the rotating shaft 30 passes through the flange hole in the flange structure and rotates relative to the flange structure. The rotating shaft 30 and the flange structure cooperate to form a friction pair. By creating a textured structure 100 on the contact surface of the rotating shaft 30 and / or the flange structure, the textured structure 100 can reduce the contact area between the rotating shaft 30 and the flange structure. During movement, the dynamic pressure effect of the textured area is enhanced, improving the load-bearing capacity of the fluid film. This causes the surfaces of the two contact surfaces to tend to separate, reducing frictional power consumption and improving the lubrication performance of the shaft and the flange inner hole. Due to the formation of a more stable fluid film, the fluid film tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between the rotating shaft 30 and the flange structure, promoting stable operation between the rotating shaft 30 and the flange structure, and increasing the service life of the rotating shaft 30 and the flange structure.

[0278] It should be noted that, in Figures 60 to 86The specific embodiments shown illustrate schemes where the textured structure 100 is provided on both the flange structure and the rotating shaft 30. In specific embodiments, the textured structure 100 can be provided on both the flange structure and the rotating shaft 30 simultaneously, or it can be provided on only one of them. Since there are many possible combinations, they will not be listed one by one. Different accompanying drawings will be provided below to illustrate the different forms of the textured structure 100.

[0279] like Figure 60 and Figure 86 As shown, the texture structure 100 consists of multiple spaced-apart textured grooves. Specifically, the texture structure 100 can be composed of spaced-apart, non-connected structures.

[0280] It should be noted that when the texture structure 100 is composed of multiple texture grooves arranged at intervals, the groove openings of the texture grooves are one or more of the following shapes: elliptical, circular, and polygonal.

[0281] Specifically, the grooves of the textured grooves can be elliptical, circular, or polygonal, arranged at intervals, or textured grooves with multiple different shapes can be arranged at intervals. Specifically, the polygon is rhomboid.

[0282] like Figures 60 to 86 In the specific embodiment shown, the flange structure includes an upper flange 50 and a lower flange 60, both of which have flange holes. The rotating shaft 30 has a long shaft section and a short shaft section. The long shaft section passes through the flange hole of the upper flange 50, and the short shaft section passes through the flange hole of the lower flange 60. At least a portion of the first contact surface is provided with a textured structure 100, and at least a portion of the second contact surface is provided with a textured structure 100.

[0283] Specifically, during the relative rotation of the shaft 30 and the flange structure, a textured structure 100 is provided between the flange structure and the shaft 30, which can enhance the load-bearing capacity of the fluid film. The enhanced fluid film effectively reduces the friction force during the rotation of the shaft 30 and the flange structure, reduces the working loss during the rotation of the shaft 30 and the flange structure, and increases the lubrication performance between the shaft 30 and the flange structure.

[0284] like Figures 60 to 86 As shown, the second contact surface includes a first region surface 301 corresponding to the long axis segment and a second region surface 302 corresponding to the short axis segment; the first contact surface includes a third region surface 501 corresponding to the upper flange 50 and a fourth region surface 601 corresponding to the lower flange 60. The first region surface 301 corresponds to the third region surface 501, and the second region surface 302 corresponds to the fourth region surface 601.

[0285] Below, based on the different textured structures 100 opened on the rotating shaft 30 or the flange structure, the following are provided: Figures 60 to 86 Multiple implementation methods.

[0286] like Figures 60 to 64 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30, and the texture structure 100 is formed on both the first region surface 301 and the second region surface 302 of the rotating shaft 30. When the texture structure 100 is composed of a plurality of texture grooves arranged at intervals, the groove opening of the texture groove is elliptical.

[0287] Specifically, the ratio between the minor axis 'a' and the major axis 'b' of the ellipse satisfies: 1.5 ≤ b / a ≤ 3.5. When the ratio between the major and minor axes of the ellipse is within the range of 1.5 to 3.5, the dynamic pressure effect of the textured region is enhanced during the relative movement of the shaft 30 and the flange structure. This strengthens the load-bearing capacity of the fluid film formed on the contact surface between the shaft 30 and the flange structure, thereby improving the lubrication performance between the shaft 30 and the flange structure and reducing frictional losses.

[0288] Specifically, the value range of the minor axis 'a' of the ellipse is 0.008mm ≤ a ≤ 0.05mm, and the value range of the major axis 'b' is 0.016mm ≤ b ≤ 0.1mm. The major and minor axes of the ellipse are within these ranges, and the ratio 1.5 ≤ b / a ≤ 3.5 is maintained. When the values ​​of the minor and major axes are too large, the elliptical textured groove becomes too large, reducing the strength of the shaft 30 and the flange structure, affecting their service life. Furthermore, an excessively large elliptical textured groove will store excess oil, which is detrimental to fluid film strength and causes oil waste. When the values ​​of the minor and major axes are too small, the amount of oil stored in the textured groove is insufficient, which is detrimental to enhancing the fluid film's load-bearing capacity. Conversely, an excessively small textured groove cannot store trace amounts of oil, which is detrimental to improving lubrication performance.

[0289] like Figure 61 As shown, the angle α between the major axis of the ellipse and the centerline of the rotating shaft 30 ranges from 10° to 60°. During the relative movement of the rotating shaft 30 with respect to the flange structure, the inclined elliptical textured groove moves in the opposite direction to the fluid film. A value of 10° to 60° ensures a strong dynamic pressure effect during the relative movement of the rotating shaft 30 with respect to the flange structure.

[0290] like Figure 62 As shown, along the axial direction of the rotation axis 30, the distance between the minor axes of two adjacent ellipses is q; along the circumferential direction of the rotation axis 30, the distance between the major axes of two adjacent ellipses is p; where q and p satisfy: 1.5≤q / p≤3.

[0291] Specifically, the distance between the two elliptical grooves is controlled by adjusting the distance between the minor axes and the major axes of two adjacent ellipses. When two adjacent elliptical grooves are too close, the excessive number of elliptical grooves reduces the strength of the shaft 30 and the flange structure, affecting their service life. When two adjacent elliptical grooves are too far apart, it is detrimental to strengthening the fluid film and reducing the friction between the shaft 30 and the flange structure. It should be noted that when the values ​​of q and p are appropriate and satisfy 1.5≤q / p≤3, it is beneficial to strengthen the load-bearing capacity of the fluid film without affecting the strength of the shaft 30 and the flange structure.

[0292] exist Figures 65 to 66 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30, and the texture structure 100 is only provided on the second region surface 302 of the second contact surface on the rotating shaft 30. The texture structure 100 is not provided on the first region surface 301 of the second contact surface on the rotating shaft 30. When the texture structure 100 is composed of multiple spaced textured grooves, it interacts with... Figure 60 and Figure 64 The specific implementation shown is similar, with the groove opening of the textured groove being elliptical. Specific parameter settings can be found in the aforementioned scheme, and will not be repeated here.

[0293] like Figures 67 to 68 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30, and the texture structure 100 is only provided on the first region surface 301 of the second contact surface on the rotating shaft 30, while the texture structure 100 is not provided on the second region surface 302 of the second contact surface on the rotating shaft 30. When the texture structure 100 is composed of multiple spaced texture grooves, it interacts with... Figure 60 and Figure 64 The specific implementation shown is similar, with the groove opening of the textured groove being elliptical. Specific parameter settings can be found in the aforementioned scheme, and will not be repeated here.

[0294] like Figures 69 to 70 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30, and the texture structure 100 is formed on both the first region surface 301 and the second region surface 302 of the rotating shaft 30. When the texture structure 100 is composed of a plurality of texture grooves arranged at intervals, the opening of the texture groove is circular.

[0295] In this embodiment, the radius R of the textured groove is in the range of 0.01mm ≤ R ≤ 0.08mm. Specifically, the radius of the textured groove should be controlled within the range of 0.01mm to 0.08mm. A radius that is too small or too large will affect the formation of the fluid film and its specific technical effect. Specifically, if the radius is too small, the oil storage capacity inside the textured groove is small, which is not conducive to enhancing the fluid film's carrying capacity. At the same time, a textured groove that is too small cannot store trace amounts of wear debris and impurities brought by the oil. If the radius is too large, it leads to a reduction in the pump body's strength, service life, and safety.

[0296] like Figures 71 to 72 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30, and the texture structure 100 is only provided on the first region surface 301 of the second contact surface on the rotating shaft 30, while the texture structure 100 is not provided on the second region surface 302 of the second contact surface on the rotating shaft 30. When the texture structure 100 is composed of multiple spaced texture grooves, it interacts with... Figure 69 and Figure 70 The specific implementation shown is similar, with the groove opening of the textured groove being circular.

[0297] like Figures 73 to 74 In the specific embodiment shown, the texture structure 100 is formed on the rotating shaft 30, and the texture structure 100 is only provided on the second region surface 302 of the second contact surface on the rotating shaft 30. The texture structure 100 is not provided on the first region surface 301 of the second contact surface on the rotating shaft 30. When the texture structure 100 is composed of multiple spaced textured grooves, it interacts with... Figure 69 and Figure 70 The specific implementation shown is similar, with the groove opening of the textured groove being circular.

[0298] like Figures 75 to 77 In the specific embodiment shown, the textured structure 100 is formed on the third region surface 501 of the upper flange 50 of the flange structure. When the textured structure 100 is composed of multiple spaced textured grooves, it interacts with... Figure 60 and Figure 64 The specific implementation shown is similar, with the groove opening of the textured groove being elliptical.

[0299] like Figures 78 to 80 In the specific embodiment shown, the textured structure 100 is formed on the third region surface 501 of the upper flange 50 of the flange structure. When the textured structure 100 is composed of multiple spaced textured grooves, it interacts with... Figure 69 and Figure 70 The specific implementation shown is similar, with the groove opening of the textured groove being circular.

[0300] like Figures 81 to 83In the specific embodiment shown, the textured structure 100 is formed on the fourth region surface 601 of the lower flange 60 of the flange structure. When the textured structure 100 is composed of multiple spaced textured grooves, it interacts with... Figure 60 and Figure 64 The specific implementation shown is similar, with the groove opening of the textured groove being elliptical.

[0301] like Figures 84 to 86 In the specific embodiment shown, the textured structure 100 is formed on the fourth region surface 601 of the lower flange 60 of the flange structure. When the textured structure 100 is composed of multiple spaced textured grooves, it interacts with... Figure 69 and Figure 70 The specific implementation shown is similar, with the groove opening of the textured groove being circular.

[0302] In addition to the above-described embodiments, the texture structure 100 may also consist of multiple intersecting texture grooves, which together form a mesh texture structure (not shown in the figure).

[0303] Specifically, the texture structure 100 consists of multiple intersecting texture grooves, which form a mesh texture structure.

[0304] When the texture structure 100 is composed of multiple intersecting texture grooves, each texture groove is one or more of straight grooves, curved grooves, and zigzag grooves. Specifically, when the texture structure 100 has an intersecting texture groove structure, the texture grooves are all of one type of straight groove, curved groove, and zigzag groove, or they can be a combination of straight grooves, curved grooves, and zigzag grooves.

[0305] Optionally, when the textured structure 100 consists of multiple intersecting textured grooves, the width of the textured grooves is between 0.02 mm and 0.16 mm. Specifically, if the width of the textured groove is too small, the oil storage capacity inside the textured groove is small, which is not conducive to enhancing the fluid film's carrying capacity. At the same time, textured grooves with too small a width cannot store trace amounts of wear debris and impurities brought by the oil. If the width of the textured groove is too large, it leads to a reduction in the strength of the pump body, as well as a reduction in service life and safety.

[0306] It should be noted that the arrangement of the texture structure 100 is not limited to the above situation. The arrangement of the texture structure 100 can also be other technical solutions that can achieve the technical effect of reducing friction and increasing sealing.

[0307] The friction pair clearance L between the first contact surface of the flange structure and the second contact surface of the rotating shaft 30 satisfies the following relationship with the depth H of the textured groove: H / L is 0.4 to 0.8. Specifically, the friction pair clearance L is greater than the depth H of the textured groove. If the friction pair clearance L is too small, the friction between the first and second contact surfaces will intensify; if the depth H of the textured groove is too small, the lubrication of the first and second contact surfaces will decrease, making it difficult to store lubricating oil. If the friction pair clearance L is too large, the fluid oil film carrying capacity will decrease; if the depth H of the textured groove is too large, it will affect the structural strength of the second contact surface and reduce the hydrodynamic lubrication effect. If the difference between the friction pair clearance L and the depth H of the textured groove is too large, it will negatively affect the lubrication effect of the friction pair surface.

[0308] The area S of the friction pair surface and the total area S1 of the region where the textured structure 100 is located satisfy the following relationship: S1 / S is 5% to 40%. The total area of ​​the region where the textured structure 100 is located includes the area of ​​all textured structures 100. If the textured structure 100 is located in only one region, the total area is the total area of ​​the textured structures 100 in that region. If the textured structure 100 is located in multiple regions, the total area is the sum of the areas of textured structures 100 in all regions. If the proportion of the total area S1 of the region where the textured structure 100 is located is too large, it will affect the overall structural strength of the shaft 30 or flange structure. Simultaneously, if the textured hole is too small, it will not achieve the effect of reducing friction. If the proportion of the total area S1 of the region where the textured structure 100 is located is too small, it will increase friction and wear under load conditions, and also increase the gap size, affecting sealing performance.

[0309] like Figure 62 As shown, the second contact surface has a textured structure 100. The distance c from the area containing the textured structure 100 to the edge of the second contact surface along the axial direction of the rotating shaft 30 ranges from 0.3 mm to c to 2 mm. If the distance between the textured area and the edge of the second contact surface of the rotating shaft 30 is too large, it is detrimental to enhancing the load-bearing capacity of the fluid film. If the distance between the textured area and the edge of the second contact surface of the rotating shaft 30 is too small, it is detrimental to the strength of the rotating shaft 30.

[0310] like Figure 58 As shown, the pump body assembly also includes a cylinder liner 40, a cylinder 10, and a piston 20. The cylinder 10 is rotatably disposed inside the cylinder liner 40, and a piston hole is provided on the cylinder 10 along its radial direction. The piston 20 is slidably disposed inside the piston hole. The rotating shaft 30 passes through the piston 20 and drives the piston 20 to reciprocate along the extension direction of the piston hole. The cylinder 10 rotates to drive the piston 20 to rotate. The flange structure is located at the axial end of the cylinder liner 40.

[0311] Specifically, during operation, the cylinder 10 rotates within the cylinder liner 40, and the piston 20 reciprocates along the piston bore extension direction. Simultaneously, the piston 20 rotates with the cylinder 10. The rotating shaft 30 provides power to the pump assembly during rotation. The flange structure is used to limit and support the rotating shaft 30 and rotate relative to the rotating shaft 30. The cylinder liner 40, cylinder 10, piston 20, and flange structure cooperate to form the pump assembly. A textured structure 100 is provided on the rotating shaft 30 and the flange structure to reduce frictional losses between the rotating shaft 30 and the flange structure.

[0312] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects:

[0313] By incorporating a textured structure 100 on the contact surface between the shaft 30 and the flange structure, the dynamic pressure effect in the textured structure 100 region is enhanced, thereby improving the lubrication performance between the shaft 30 and the flange structure and preventing problems such as shaft 30 wear, shaft 30 breakage, and flange structure wear. Currently, the existing pump body's shaft 30 provides the power source for the pump body, and the flange structure supports the shaft 30. During operation, the shaft 30 will generate friction with the flange structure. Especially when the pump body components and fluid machinery operate under heavy-duty, high-frequency conditions, the friction between the shaft 30 and the flange structure will intensify, leading to problems such as shaft 30 wear, breakage, and flange shaft hole wear.

[0314] Specifically, the rotating shaft 30 passes through the flange hole in the flange structure and rotates relative to the flange structure. The rotating shaft 30 and the flange structure cooperate to form a friction pair. By creating a textured structure 100 on the contact surface of the rotating shaft 30 and / or the flange structure, the textured structure 100 can reduce the contact area between the rotating shaft 30 and the flange structure. During movement, the dynamic pressure effect of the textured area is enhanced, improving the load-bearing capacity of the fluid film. This causes the surfaces of the two contact surfaces to tend to separate, reducing frictional power consumption and improving the lubrication performance of the shaft and the flange inner hole. Due to the formation of a more stable fluid film, the fluid film tightly adheres to the surfaces of the two contact surfaces, improving the sealing performance between the rotating shaft 30 and the flange structure, promoting stable operation between the rotating shaft 30 and the flange structure, and increasing the service life of the rotating shaft 30 and the flange structure.

[0315] Obviously, the embodiments described above are merely some, not all, embodiments of the present invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort should fall within the scope of protection of the present invention.

[0316] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0317] It should be noted that the terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in sequences other than those illustrated or described herein.

[0318] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A pump body assembly, characterized by, include: Cylinder liner (40), the cylinder liner (40) having a volume chamber (4001); A cylinder (10) is rotatably disposed in the volume chamber (4001), and the rotation center of the cylinder (10) coincides with the center of the volume chamber (4001). The outer peripheral surface of the cylinder (10) is adapted to the inner surface of the cylinder liner (40). The outer peripheral surface of the cylinder (10) is a first contact surface (1001), and the inner surface of the cylinder liner (40) is a second contact surface (4002). The first contact surface (1001) and the second contact surface (4002) form a friction pair surface. A textured structure (100) is provided on the first contact surface (1001) and / or the second contact surface (4002). The area S of the friction pair surface and the total area S1 of the region where the texture structure (100) is located satisfy the following: S1 / S is 5% to 15%; The textured structure (100) is provided on the contact surface between the cylinder (10) and the piston (20) of the pump body assembly. The texture structure (100) is composed of a plurality of spaced texture grooves; or the texture structure (100) is composed of a plurality of cross-arranged texture grooves, the plurality of cross-arranged texture grooves forming a mesh texture structure.

2. The pump body assembly according to claim 1, characterized in that, When the texture structure (100) is composed of a plurality of spaced texture grooves, the groove openings of the texture grooves are one or more of elliptical, circular, and polygonal shapes; When the texture structure (100) is composed of a plurality of texture grooves arranged in a cross pattern, each texture groove is one or more of a straight groove, a curved groove, and a broken groove.

3. The pump body assembly of claim 2, wherein, When the opening of the textured groove is circular, the equivalent diameter of the textured groove is 0.02 mm to 0.5 mm.

4. The pump body assembly of claim 2, wherein, When the texture structure (100) is composed of a plurality of cross-arranged texture grooves, the width of the texture grooves is 0.02 mm to 0.5 mm.

5. The pump body assembly according to claim 2, characterized in that, When the groove opening of the textured groove is elliptical, the minor axis a of the ellipse and the major axis b of the ellipse satisfy the following condition: 1.5 ≤ b / a ≤ 3.

5.

6. The pump body assembly according to claim 5, characterized in that, The value range of the minor axis 'a' of the ellipse is 0.008 mm ≤ a ≤ 0.05 mm; and / or The range of the major axis b of the ellipse is 0.016mm ≤ b ≤ 0.1mm.

7. The pump body assembly according to claim 2, characterized in that, When the groove opening of the textured groove is elliptical, the center distance k between two adjacent ellipses and the major axis b of the ellipse satisfy the following condition: 2.5 ≤ k / b ≤ 5.

8. The pump body assembly according to claim 1, characterized in that, The friction pair gap L between the first contact surface (1001) and the second contact surface (4002) satisfies the following relationship with the depth H of the textured groove: H / L is 0.4 to 0.

8.

9. The pump body assembly according to claim 2, characterized in that, When the texture structure (100) is composed of a plurality of spaced textured grooves, the center line of the texture structure (100) is perpendicular to the rotation center line of the cylinder (10).

10. The pump body assembly according to any one of claims 1 to 9, characterized in that, The first contact surface (1001) has the textured structure (100), and the distance L from the area where the textured structure (100) is located to the edge of the first contact surface (1001) in the direction of the rotation center line of the cylinder (10) is greater than or equal to 2.5 mm.

11. The pump body assembly according to any one of claims 1 to 9, characterized in that, The cylinder (10) has a piston hole (106) along its radial direction, and the textured structure (100) is provided on the first contact surface (1001). The radius Rb of the area of ​​the textured structure (100) at the edge of the piston hole (106) satisfies the following condition: Rb-Ra is greater than or equal to 2.5mm.

12. The pump body assembly according to any one of claims 1 to 9, characterized in that, The textured structure (100) is provided on at least a portion of the first contact surface (1001); and / or The textured structure (100) is provided on at least a portion of the second contact surface (4002).

13. The pump body assembly according to claim 12, characterized in that, The textured structure (100) is provided at various locations on the first contact surface (1001); The texture structure (100) is provided in a portion of the second contact surface (4002).

14. The pump body assembly according to claim 13, characterized in that, The cylinder liner (40) has an intake passage and an exhaust passage. The intake passage is located on the intake side of the cylinder liner (40), and the exhaust passage is located on the exhaust side of the cylinder liner (40). The textured structure (100) is not provided on the area of ​​the second contact surface (4002) on the intake side.

15. A fluid machine, characterized in that, Includes the pump body assembly according to any one of claims 1 to 14.

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