Pump body structure, compressor and refrigeration equipment

Abstract

The invention relates to a pump body structure, a compressor and refrigeration equipment, and relates to the technical field of refrigeration equipment. The compressor comprises an air cylinder assembly, a crankshaft and a roller. The crankshaft is rotatably arranged in the air cylinder assembly in a penetrating mode. The roller is arranged on the crankshaft and located in the air cylinder assembly, the roller is driven by the crankshaft to roll along the cylinder wall of the air cylinder assembly, and the roller makes contact with the cylinder wall of the air cylinder assembly to jointly form a working cavity. The air cylinder assembly, the crankshaft and the roller are all made of light materials with the density smaller than that of iron-based alloy, and the absolute value of the difference of the linear expansion coefficients of any two of the air cylinder assembly, the crankshaft and the roller is not larger than a preset difference value, so that the preset gap among the air cylinder assembly, the crankshaft and the roller is kept stable. According to the technical scheme, the linear expansion coefficients of the air cylinder assembly, the crankshaft and the roller can be kept consistent while the weight of the pump body is reduced, and the stability of the preset gap is guaranteed.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration equipment, and in particular to a pump body structure, a compressor and a refrigeration equipment. Background Art

[0002] The compressor is the core component of the refrigeration equipment. The capacity and characteristics of the compressor determine the capacity and characteristics of the refrigeration equipment. Among them, the lightweighting of the compressor facilitates the weight reduction of the refrigeration equipment. Existing compressors generally use iron-based materials, such as cast iron and steel. In some cases, the lightweighting solution for the compressor is to replace some parts such as the rollers and crankshafts of the pump body. By replacing the iron-based materials with lightweight aluminum alloy materials, it is not only beneficial to the balance of the pump body shaft system, but also can improve noise and enhance the stability of the compressor; but due to the different thermal expansion coefficients of different materials, the thermal coupling deformation caused by temperature changes causes the preset clearance between the rollers and the flange and crankshaft to change, resulting in increased roller wear and even jamming, affecting the reliability of the compressor. Summary of the invention

[0003] The embodiments of the present invention provide a pump body structure, a compressor and a refrigeration device, which can achieve lightweighting of the pump body while keeping the linear expansion coefficients of the cylinder assembly, the crankshaft and the roller consistent, thereby ensuring the stability of the preset gap.

[0004] In a first aspect, an embodiment of the present invention provides a compressor, comprising:

[0005] Cylinder assembly;

[0006] A crankshaft rotatably inserted into the cylinder assembly; and

[0007] A roller, arranged on the crankshaft and located in the cylinder assembly, wherein the roller rolls along the cylinder wall of the cylinder assembly under the drive of the crankshaft and contacts the cylinder wall of the cylinder assembly to form a working chamber together;

[0008] Among them, the cylinder assembly, the crankshaft, and the roller are all made of lightweight materials with a density lower than that of iron-based alloys, and the absolute value of the difference in linear expansion coefficients of any two of the cylinder assembly, the crankshaft, and the roller is not greater than a preset difference, so that the preset gap between the cylinder assembly, the crankshaft, and the roller remains stable.

[0009] In one embodiment, the lightweight material is aluminum alloy, and the cylinder assembly, the crankshaft and the roller are all made of aluminum alloy.

[0010] In one embodiment, the lightweight material is aluminum alloy or polymer; wherein the cylinder assembly and the crankshaft are both made of aluminum alloy, and the roller is made of polymer, and the density of the roller is less than that of the aluminum alloy.

[0011] In one embodiment, an air intake hole and an air exhaust hole are provided on the cylinder wall of the cylinder assembly; wherein, a heat insulating member is also provided on the cylinder wall of the cylinder assembly, and the heat insulating member is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole.

[0012] In one embodiment, along the fluid compression direction, the cutoff angle of the thermal insulation element is 200°-340°.

[0013] In one embodiment, the cylinder assembly comprises:

[0014] Cylinder body;

[0015] an upper flange, disposed at one end of the cylinder body; and

[0016] A lower flange is arranged at the other end of the cylinder body;

[0017] Wherein, the crankshaft is rotatably connected to the upper flange and the lower flange respectively, and the air intake hole, the air exhaust hole and the heat insulation component are all arranged on the cylinder wall of the cylinder body.

[0018] In one embodiment, a groove is provided inside the cylinder wall of the cylinder body or on the inner surface of the cylinder wall of the cylinder body, and the groove is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the suction port, wherein the thermal insulation member is arranged in the groove.

[0019] In one embodiment, the thickness of the thermal insulation is 2 mm.

[0020] In one embodiment, the roller is a hollow structure.

[0021] In one embodiment, the pump body structure also includes a slide vane, which is movably disposed on the cylinder assembly and is always in contact with the roller to separate the working chamber into an intake chamber and a compression chamber; wherein the intake hole and the exhaust hole are respectively located on both sides of the slide vane.

[0022] In one embodiment, the sliding vane is a ceramic sliding vane, or the sliding vane is an aluminum alloy sliding vane and the sliding vane is a hollow structure.

[0023] In a second aspect, an embodiment of the present invention provides a compressor, comprising a housing and a pump body structure as described above, wherein the pump body structure is disposed in the housing.

[0024] In one embodiment, the housing is made of aluminum alloy.

[0025] In one embodiment, the refrigerant used by the compressor is R290 or R32.

[0026] In a third aspect, an embodiment of the present invention provides a refrigeration device, comprising the compressor as described above.

[0027] Compared with the prior art, the advantage of the embodiments of the present invention is that by using lightweight materials with a density lower than that of iron-based alloys to make cylinder assemblies, crankshafts, and rollers, the weight of the pump body structure is reduced, thereby achieving lightweight compressors; at the same time, the weight reduction of rollers and crankshafts is not only beneficial to the shaft balance of the pump body structure, but also can improve vibration noise and enhance the stability of the compressor. By setting the absolute value of the difference between the linear expansion coefficients of any two of the cylinder assemblies, crankshafts, and rollers to be no greater than the preset difference, the linear expansion coefficients of the cylinder assemblies, crankshafts, and rollers are kept consistent, thereby solving the problem that the preset clearance of the friction pair between the cylinder assembly 10, crankshaft, and rollers changes due to inconsistent linear expansion coefficients, resulting in increased friction and wear, and even jamming and leakage, thereby ensuring the stability of the preset clearance. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] Hereinafter, the present invention will be described in more detail based on embodiments and with reference to the accompanying drawings.

[0029] Figure 1 is a structural schematic diagram of a pump body structure provided by an embodiment of the present invention;

[0030] Figure 2 yes Figure 1 A schematic diagram of the three-dimensional structure of a cylinder body provided in the embodiment;

[0031] Figure 3 yes Figure 1 A top view of a cylinder body provided in the embodiment;

[0032] Figure 4 yes Figure 1 A schematic diagram of the structure of the heat insulation member provided in the embodiment;

[0033] Figure 5 is a schematic diagram of the three-dimensional structure of a cylinder body provided by another embodiment of the present invention;

[0034] Figure 6 yes Figure 5 A top view of a cylinder body provided in the embodiment;

[0035] Figure 7 yes Figure 5 A schematic diagram of the structure of the heat insulation member provided in the embodiment;

[0036] Figure 8 yes Figure 1 A schematic structural diagram of a roller provided in the embodiment;

[0037] Fig. 9 yes Figure 1 A schematic diagram of the structure of a slide provided in the embodiment;

[0038] Fig.10 Schematic diagram of the structure of a compressor provided by another embodiment of the present invention

[0039] Fig.11 yes Fig.10 The embodiment in the figure is applicable to the stress simulation diagram of the R32 refrigerant application scenario;

[0040] Fig.12 yes Fig.10 The embodiment in the figure is applicable to the stress simulation diagram of the R290 refrigerant application scenario.

[0041] Reference numerals:

[0042] 1. Pump structure; 2. Shell; 3. Liquid reservoir; 4. Motor;

[0043] 10. Cylinder assembly; 110. Air intake hole; 120. Air exhaust hole; 130. Cylinder body; 1301. Groove; 1302. Slide groove; 1303. Cylinder hole; 140. Upper flange; 150. Lower flange;

[0044] 20. Crankshaft;

[0045] 30. Roller;

[0046] 40. Thermal insulation;

[0047] 50. Slide. DETAILED DESCRIPTION

[0048] The present invention will be further described below in conjunction with the accompanying drawings.

[0049] The compressor is the core component of the refrigeration equipment. The capacity and characteristics of the compressor determine the capacity and characteristics of the refrigeration equipment. Among them, the lightweighting of the compressor facilitates the weight reduction of the refrigeration equipment. Existing compressors generally use iron-based materials, such as cast iron and steel. In some cases, the lightweighting solution for the compressor is to replace some parts of the pump body, such as rollers and crankshafts, with lightweight aluminum alloy materials to replace iron-based materials. Compared with iron-based materials, the advantages of aluminum alloys are low density and fast heat transfer, but the disadvantages are high friction coefficient, low surface hardness, low strength, poor wear resistance, and large linear expansion coefficient. Therefore, the use of aluminum alloy materials for replacement is not only conducive to the balance of the pump body shaft system, but also can improve noise and enhance the stability of the compressor; but due to the different thermal expansion coefficients of different materials, the linear expansion coefficient of aluminum alloy is much greater than that of cast iron, and temperature changes will cause deformation. According to the formula L = L0 (1 + αΔT), under the same temperature rise ΔT and the same size L0, the linear expansion coefficient of aluminum alloy (taking deformed aluminum 4032 as an example, α (100℃) ≈ 20.7×10 -6 K -1 ) is about cast iron (taking HT250 as an example, α(100℃)≈10.8×10 -6 K -1 ), the thermal coupling deformation caused by temperature change causes the preset clearance between the roller and the flange and crankshaft to change, resulting in increased roller wear or even jamming, affecting the reliability of the compressor.

[0050] Embodiment 1

[0051] like Figure 1 As shown, in order to solve the above technical problems, an embodiment of the present invention provides a pump body structure, including a cylinder assembly 10, a crankshaft 20 and a roller 30; the crankshaft 20 is rotatably arranged in the cylinder assembly 10; the roller 30 is arranged on the crankshaft 20 and is located in the cylinder assembly 10, and the roller 30 rolls along the cylinder wall of the cylinder assembly 10 under the drive of the crankshaft 20, and contacts with the cylinder wall of the cylinder assembly 10 to jointly form a working chamber; wherein, the cylinder assembly 10, the crankshaft 20, and the roller 30 are all made of lightweight materials with a density less than that of the iron-based alloy, and the absolute value of the difference in linear expansion coefficients of any two of the cylinder assembly 10, the crankshaft 20, and the roller 30 is not greater than the preset difference, so that the preset gap between the cylinder assembly 10, the crankshaft 20, and the roller 30 remains stable.

[0052] As can be seen from the above, by using lightweight materials with a density lower than that of iron-based alloys to make the cylinder assembly 10, crankshaft 20, and roller 30, the weight reduction effect is achieved, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor; at the same time, the weight reduction of the roller 30 and the crankshaft 20 is not only beneficial to the shaft balance of the pump body structure, but also can improve vibration noise and enhance the stability of the compressor. By setting the absolute value of the difference between the linear expansion coefficients of any two of the cylinder assembly 10, crankshaft 20, and roller 30 to be no greater than the preset difference, the linear expansion coefficients of the cylinder assembly 10, crankshaft 20, and roller 30 are kept consistent, and the problem of changes in the preset clearance of the friction pair between the cylinder assembly 10, crankshaft 20, and roller 30 due to inconsistent linear expansion coefficients is solved, resulting in increased friction and wear, and even jamming and leakage, thereby ensuring the stability of the preset clearance.

[0053] It should be noted that the crankshaft 20 can rotate under the drive of the motor 4, thereby driving the roller 30 to rotate; an eccentric portion is provided on the crankshaft 20, and the roller 30 is provided on the eccentric portion; the crankshaft 20 drives the rotor to rotate, so that the volume in the working chamber changes periodically, completing the intake and exhaust and compression processes, wherein the shape of the working chamber is crescent-shaped.

[0054] It should also be noted that the preset difference is h / (150L0)×10 -6 K -1 , where h is the preset clearance, unit: μm, such as the clearance between the roller end face and the flange end face. The preset clearance h is determined by the assembly requirements of the parts; L0 is the characteristic dimension, unit: m, such as the roller diameter, crankshaft diameter, roller height, etc. For example, the roller height is 0.020m, the preset clearance between the roller end face and the flange end face is 11μm, then the preset difference in linear expansion coefficients of the two materials is 3.67×10 -6 K -1 ;

[0055] Specifically, different characteristic dimensions need to be selected for preset clearances at different positions. The characteristic dimensions are related dimensions that cause the preset clearance to change under the influence of linear expansion. For example, if the clearance between the roller end face and the flange end face is affected by the linear expansion in the axial direction, the roller height is selected as the characteristic dimension; if the clearance between the roller inner bore cylindrical surface and the crankshaft eccentric part is affected by the linear expansion of the roller inner diameter, the roller inner diameter is selected as the characteristic dimension; if the clearance between the roller outer cylindrical surface and the inner wall of the cylinder is affected by the linear expansion of the roller outer diameter, the roller outer diameter is selected as the characteristic dimension.

[0056] Therefore, the materials of the cylinder assembly, crankshaft, and roller need to satisfy the preset gaps at different positions and the preset differences calculated from the corresponding characteristic dimensions.

[0057] It should also be noted that iron-based materials are materials with iron as the main component, and iron-based materials include iron-based alloys, such as cast iron and steel.

[0058] It should also be noted that the number of the roller 30 may be one or more, and the plurality of rollers 30 are arranged at intervals along the axial direction of the crankshaft 20 .

[0059] Embodiment 2

[0060] like Figure 1 As shown, an embodiment of the present invention provides a pump body structure, including a cylinder assembly 10, a crankshaft 20 and a roller 30; the crankshaft 20 is rotatably arranged in the cylinder assembly 10; the roller 30 is arranged on the crankshaft 20 and is located in the cylinder assembly 10, and the roller 30 rolls along the cylinder wall of the cylinder assembly 10 under the drive of the crankshaft 20, and contacts with the cylinder wall of the cylinder assembly 10 to jointly form a working chamber; wherein, the cylinder assembly 10, the crankshaft 20, and the roller 30 are all made of lightweight materials with a density less than that of the iron-based alloy, and the absolute value of the difference in linear expansion coefficients of any two of the cylinder assembly 10, the crankshaft 20, and the roller 30 is not greater than the preset difference, so that the preset gap between the cylinder assembly 10, the crankshaft 20, and the roller 30 remains stable.

[0061] As can be seen from the above, by using lightweight materials with a density lower than that of iron-based alloys to make the cylinder assembly 10, crankshaft 20, and roller 30, the weight reduction effect is achieved, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor; at the same time, the weight reduction of the roller 30 and the crankshaft 20 is not only beneficial to the shaft balance of the pump body structure, but also can improve vibration noise and enhance the stability of the compressor. By setting the absolute value of the difference between the linear expansion coefficients of any two of the cylinder assembly 10, crankshaft 20, and roller 30 to be no greater than the preset difference, the linear expansion coefficients of the cylinder assembly 10, crankshaft 20, and roller 30 are kept consistent, and the problem of changes in the preset clearance of the friction pair between the cylinder assembly 10, crankshaft 20, and roller 30 due to inconsistent linear expansion coefficients is solved, resulting in increased friction and wear, and even jamming and leakage, thereby ensuring the stability of the preset clearance.

[0062] It should be noted that the crankshaft 20 can rotate under the drive of the motor 4, thereby driving the roller 30 to rotate; an eccentric portion is provided on the crankshaft 20, and the roller 30 is provided on the eccentric portion; the crankshaft 20 drives the rotor to rotate, so that the volume in the working chamber changes periodically, completing the intake and exhaust and compression processes, wherein the shape of the working chamber is crescent-shaped.

[0063] It should also be noted that iron-based materials are materials with iron as the main component, and iron-based materials include iron-based alloys, such as cast iron and steel.

[0064] It should also be noted that the number of the roller 30 may be one or more, and the plurality of rollers 30 are arranged at intervals along the axial direction of the crankshaft 20 .

[0065] In some embodiments, the lightweight material is aluminum alloy, and the cylinder assembly 10, the crankshaft 20 and the roller 30 are all made of aluminum alloy.

[0066] By using aluminum alloy materials to prepare the cylinder assembly 10, the crankshaft 20 and the roller 30, on the one hand, the lightweight effect of aluminum alloy is fully utilized, thereby reducing the weight of the pump body structure and realizing lightweight compressor. On the other hand, the heat transfer and heat dissipation advantages of aluminum alloy materials are utilized to reduce the temperature rise during the compression process and improve the compression efficiency.

[0067] It should be noted that aluminum alloys are divided into two categories according to the molding method, namely, deformed aluminum and die-cast aluminum; the cylinder assembly 10, the roller 30, the crankshaft 20 and the vane 50 can be made of deformed aluminum or die-cast aluminum, and the types of aluminum alloys used by the cylinder assembly 10, the roller 30, the crankshaft 20 and the vane 50 can be the same or different, and the selection is made according to actual needs, and this application does not make specific restrictions. For example, the crankshaft 20 can be made of deformed aluminum 4032, which has higher strength than cast aluminum; the upper flange 140 and the lower flange 150 are made of cast aluminum YL113, which has fast molding and high utilization rate; the roller 30 and the vane 50 are made of 7 series super-hard aluminum alloy 7075.

[0068] In some embodiments, the lightweight material is aluminum alloy or polymer; wherein the cylinder assembly 10 and the crankshaft 20 are both made of aluminum alloy, and the roller 30 is made of polymer, and the density of the roller 30 is less than that of the aluminum alloy.

[0069] By using aluminum alloy materials to prepare the cylinder assembly 10 and the crankshaft 20, on the one hand, the lightweight effect of aluminum alloy is fully utilized, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor. On the other hand, the heat transfer and heat dissipation advantages of aluminum alloy materials are utilized to reduce the temperature rise during the compression process and improve the compression efficiency. The roller 30 is prepared by polymer, so that the roller 30 can meet the lightweight design while keeping the linear expansion coefficient of the roller 30 consistent with the linear expansion coefficient of the cylinder assembly 10 and the crankshaft 20, thereby avoiding problems such as wear, jamming, and leakage caused by excessive differences in linear expansion coefficients, and ensuring the stability of the preset gap.

[0070] It should be noted that the polymer includes but is not limited to polyethersulfone (PES), polyimide (PI), and polyetheretherketone (PEEK).

[0071] Embodiment 3

[0072] like Figure 1As shown, an embodiment of the present invention provides a pump body structure, including a cylinder assembly 10, a crankshaft 20 and a roller 30; the crankshaft 20 is rotatably arranged in the cylinder assembly 10; the roller 30 is arranged on the crankshaft 20 and is located in the cylinder assembly 10, and the roller 30 rolls along the cylinder wall of the cylinder assembly 10 under the drive of the crankshaft 20, and contacts with the cylinder wall of the cylinder assembly 10 to jointly form a working chamber; wherein, the cylinder assembly 10, the crankshaft 20, and the roller 30 are all made of lightweight materials with a density less than that of the iron-based alloy, and the absolute value of the difference in linear expansion coefficients of any two of the cylinder assembly 10, the crankshaft 20, and the roller 30 is not greater than the preset difference, so that the preset gap between the cylinder assembly 10, the crankshaft 20, and the roller 30 remains stable.

[0073] As can be seen from the above, by using lightweight materials with a density lower than that of iron-based alloys to make the cylinder assembly 10, crankshaft 20, and roller 30, the weight reduction effect is achieved, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor; at the same time, the weight reduction of the roller 30 and the crankshaft 20 is not only beneficial to the shaft balance of the pump body structure, but also can improve vibration noise and enhance the stability of the compressor. By setting the absolute value of the difference between the linear expansion coefficients of any two of the cylinder assembly 10, crankshaft 20, and roller 30 to be no greater than the preset difference, the linear expansion coefficients of the cylinder assembly 10, crankshaft 20, and roller 30 are kept consistent, and the problem of changes in the preset clearance of the friction pair between the cylinder assembly 10, crankshaft 20, and roller 30 due to inconsistent linear expansion coefficients is solved, resulting in increased friction and wear, and even jamming and leakage, thereby ensuring the stability of the preset clearance.

[0074] It should be noted that the crankshaft 20 can rotate under the drive of the motor 4, thereby driving the roller 30 to rotate; an eccentric portion is provided on the crankshaft 20, and the roller 30 is provided on the eccentric portion; the crankshaft 20 drives the rotor to rotate, so that the volume in the working chamber changes periodically, completing the intake and exhaust and compression processes, wherein the shape of the working chamber is crescent-shaped.

[0075] It should also be noted that iron-based materials are materials with iron as the main component, and iron-based materials include iron-based alloys, such as cast iron and steel.

[0076] It should also be noted that the number of the roller 30 may be one or more, and the plurality of rollers 30 are arranged at intervals along the axial direction of the crankshaft 20 .

[0077] In some embodiments, the lightweight material is aluminum alloy, and the cylinder assembly 10, the crankshaft 20 and the roller 30 are all made of aluminum alloy.

[0078] By using aluminum alloy materials to prepare the cylinder assembly 10, the crankshaft 20 and the roller 30, on the one hand, the lightweight effect of aluminum alloy is fully utilized, thereby reducing the weight of the pump body structure and realizing lightweight compressor. On the other hand, the heat transfer and heat dissipation advantages of aluminum alloy materials are utilized to reduce the temperature rise during the compression process and improve the compression efficiency.

[0079] It should be noted that aluminum alloys are divided into two categories according to the molding method, namely, deformed aluminum and die-cast aluminum; the cylinder assembly 10, the roller 30, the crankshaft 20 and the vane 50 can be made of deformed aluminum or die-cast aluminum, and the types of aluminum alloys used by the cylinder assembly 10, the roller 30, the crankshaft 20 and the vane 50 can be the same or different, and the selection is made according to actual needs, and this application does not make specific restrictions. For example, the crankshaft 20 can be made of deformed aluminum 4032, which has higher strength than cast aluminum; the upper flange 140 and the lower flange 150 are made of cast aluminum YL113, which has fast molding and high utilization rate; the roller 30 and the vane 50 are made of 7 series super-hard aluminum alloy 7075.

[0080] In some embodiments, the lightweight material is aluminum alloy or polymer; wherein the cylinder assembly 10 and the crankshaft 20 are both made of aluminum alloy, and the roller 30 is made of polymer, and the density of the roller 30 is less than that of the aluminum alloy.

[0081] By using aluminum alloy materials to prepare the cylinder assembly 10 and the crankshaft 20, on the one hand, the lightweight effect of aluminum alloy is fully utilized, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor. On the other hand, the heat transfer and heat dissipation advantages of aluminum alloy materials are utilized to reduce the temperature rise during the compression process and improve the compression efficiency. By using polymers to prepare the roller 30, the roller 30 can meet the lightweight design while keeping the linear expansion coefficient of the roller 30 consistent with the linear expansion coefficient of the cylinder assembly 10 and the crankshaft 20, thereby avoiding problems such as wear, jamming, and leakage caused by excessive differences in linear expansion coefficients, and ensuring the stability of the preset gap.

[0082] It should be noted that the polymer includes but is not limited to polyethersulfone (PES), polyimide (PI), and polyetheretherketone (PEEK).

[0083] like Figure 2-Figure 7 As shown, in some embodiments, an air intake hole 110 and an air intake hole 110 are provided on the cylinder wall of the cylinder assembly 10; wherein, a heat insulating member 40 is also provided on the cylinder wall of the cylinder assembly 10, and the heat insulating member 40 is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110.

[0084] The air intake and exhaust of the pump structure are realized by setting the air intake holes 110 and the air intake holes 110 respectively; the heat insulation 40 is set on the cylinder wall to play a heat insulation role, reduce the rise of the suction temperature, and ensure the refrigeration capacity of the compressor. In addition, the heat insulation 40 is set on the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110. This is because the air intake process needs to be insulated to avoid overheating of the refrigerant, resulting in a reduction in the air intake volume and a decrease in the refrigeration capacity. The compression process is an important source of temperature rise. Therefore, the heat insulation 40 is not set in the compression process, so that the heat can be transferred to the pump structure, and the aluminum alloy cylinder assembly 10 is used to quickly dissipate heat to improve the heat dissipation effect.

[0085] It should be noted that the fluid compression direction refers to the rotation direction of the crankshaft 20, which is the clockwise direction in this embodiment.

[0086] It should also be noted that the cylinder assembly 10 has five characteristic angles, namely, the front edge angle of the air intake hole 110, the rear edge angle of the air intake hole 110, the front edge angle of the air intake hole 110, the rear edge angle of the air intake hole 110 and the exhaust start angle. When the rotor rotates to different characteristic angles, it corresponds to different states; among them, Figure 3 As shown, the rear edge angle of the suction hole 110 is α, and the suction starts when the rotor rotates clockwise to the rear edge angle α of the suction hole 110; the exhaust starting angle is β, and when the rotor rotates clockwise to the exhaust starting angle β, the exhaust pressure is reached and the exhaust starts;

[0087] In addition, when the rotor starts to rotate from 0° to 2°, the process from the edge angle α behind the intake hole 110 to 2° is the intake process; when the rotor starts the second rotation, that is, the process from the rotor starts to rotate from 2° to 4°, the process from 2° + the front edge angle of the intake hole 110 to 2° + the exhaust starting angle β is the compression process, at which time the pressure rises, and the process from 2° + the exhaust starting angle β to 4° - the rear edge angle of the intake hole 110 is the exhaust process.

[0088] It should also be noted that the heat insulation component can be provided on the entire section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110, or can be provided on only a part of the section.

[0089] In some embodiments, the cutoff angle of the thermal insulation 40 along the fluid compression direction is 200°-340°.

[0090] By setting the cut-off angle to 200°-340° and limiting the interval range of the heat insulating member 40, it is not only ensured that the heat insulating member 40 can be applied to different working conditions of the compressor, but also ensured that the heat insulating member 40 can avoid the area where the air intake hole 110 is located. Because the exhaust angle of the compressor is different under different working conditions, when the cut-off angle is less than 200°, the heat insulating member 40 cannot meet the requirements of different working conditions of the compressor; when the cut-off angle is greater than 340°, the heat insulating member 40 will interfere with the area of ​​the air intake hole 110, resulting in partial obstruction of the air intake hole 110.

[0091] It should be noted that if Figure 2 , Figure 3 As shown, the two sides of the thermal insulation member 40 are respectively a first side and a second side, the first side is the side of the thermal insulation member 40 close to the exhaust starting angle β, and the second side is the side of the thermal insulation member 40 away from the exhaust starting angle β. The cut-off angle of the thermal insulation member 40, that is, when the rotor rotates from the vane 50 along the fluid compression direction to the second side of the thermal insulation member 40, the rotation angle is 200°-340°; in addition, the angle between the second side of the thermal insulation member 40 and the vane 50 is θ, θ is 20°-160°, and when the cut-off angle is 340°, θ is 20°, thereby ensuring that the thermal insulation member 40 can avoid the area where the suction hole 110 is located.

[0092] Embodiment 4

[0093] like Figure 1 As shown, an embodiment of the present invention provides a pump body structure, including a cylinder assembly 10, a crankshaft 20 and a roller 30; the crankshaft 20 is rotatably arranged in the cylinder assembly 10; the roller 30 is arranged on the crankshaft 20 and is located in the cylinder assembly 10, and the roller 30 rolls along the cylinder wall of the cylinder assembly 10 under the drive of the crankshaft 20, and contacts with the cylinder wall of the cylinder assembly 10 to jointly form a working chamber; wherein, the cylinder assembly 10, the crankshaft 20, and the roller 30 are all made of lightweight materials with a density less than that of the iron-based alloy, and the absolute value of the difference in linear expansion coefficients of any two of the cylinder assembly 10, the crankshaft 20, and the roller 30 is not greater than the preset difference, so that the preset gap between the cylinder assembly 10, the crankshaft 20, and the roller 30 remains stable.

[0094] As can be seen from the above, by using lightweight materials with a density lower than that of iron-based alloys to make the cylinder assembly 10, crankshaft 20, and roller 30, the weight reduction effect is achieved, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor; at the same time, the weight reduction of the roller 30 and the crankshaft 20 is not only beneficial to the shaft balance of the pump body structure, but also can improve vibration noise and enhance the stability of the compressor. By setting the absolute value of the difference between the linear expansion coefficients of any two of the cylinder assembly 10, crankshaft 20, and roller 30 to be no greater than the preset difference, the linear expansion coefficients of the cylinder assembly 10, crankshaft 20, and roller 30 are kept consistent, and the problem of changes in the preset clearance of the friction pair between the cylinder assembly 10, crankshaft 20, and roller 30 due to inconsistent linear expansion coefficients is solved, resulting in increased friction and wear, and even jamming and leakage, thereby ensuring the stability of the preset clearance.

[0095] It should be noted that the crankshaft 20 can rotate under the drive of the motor 4, thereby driving the roller 30 to rotate; an eccentric portion is provided on the crankshaft 20, and the roller 30 is provided on the eccentric portion; the crankshaft 20 drives the rotor to rotate, so that the volume in the working chamber changes periodically, completing the intake and exhaust and compression processes, wherein the shape of the working chamber is crescent-shaped.

[0096] It should also be noted that iron-based materials are materials with iron as the main component, and iron-based materials include iron-based alloys, such as cast iron and steel.

[0097] It should also be noted that the number of the roller 30 may be one or more, and the plurality of rollers 30 are arranged at intervals along the axial direction of the crankshaft 20 .

[0098] In some embodiments, the lightweight material is aluminum alloy, and the cylinder assembly 10, the crankshaft 20 and the roller 30 are all made of aluminum alloy.

[0099] By using aluminum alloy materials to prepare the cylinder assembly 10 and the crankshaft 20, on the one hand, the lightweight and weight-reducing effect of aluminum alloy can be fully utilized, thereby reducing the weight of the pump body structure and achieving lightweight compressor. On the other hand, the heat transfer and heat dissipation advantages of aluminum alloy materials are utilized to reduce the temperature rise during the compression process and improve the compression efficiency.

[0100] It should be noted that aluminum alloys are divided into two categories according to the molding method, namely, deformed aluminum and die-cast aluminum; the cylinder assembly 10, the roller 30, the crankshaft 20 and the vane 50 can be made of deformed aluminum or die-cast aluminum, and the types of aluminum alloys used by the cylinder assembly 10, the roller 30, the crankshaft 20 and the vane 50 can be the same or different, and the selection is made according to actual needs, and this application does not make specific restrictions. For example, the crankshaft 20 can be made of deformed aluminum 4032, which has higher strength than cast aluminum; the upper flange 140 and the lower flange 150 are made of cast aluminum YL113, which has fast molding and high utilization rate; the roller 30 and the vane 50 are made of 7 series super-hard aluminum alloy 7075.

[0101] In some embodiments, the lightweight material is aluminum alloy or polymer; wherein the cylinder assembly 10 and the crankshaft 20 are both made of aluminum alloy, and the roller 30 is made of polymer, and the density of the roller 30 is less than that of the aluminum alloy.

[0102] By using aluminum alloy materials to prepare the cylinder assembly 10, the crankshaft 20 and the roller 30, on the one hand, the lightweight effect of aluminum alloy is fully utilized, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor, and on the other hand, the heat transfer and heat dissipation advantages of aluminum alloy materials are utilized to reduce the temperature rise during the compression process and improve the compression efficiency. By using polymers to prepare the roller 30, the roller 30 can meet the lightweight design while keeping the linear expansion coefficient of the roller 30 consistent with the linear expansion coefficient of the cylinder assembly 10 and the crankshaft 20, thereby avoiding problems such as wear, jamming, and leakage caused by excessive differences in linear expansion coefficients, and ensuring the stability of the preset gap.

[0103] It should be noted that the polymer includes but is not limited to polyethersulfone (PES), polyimide (PI), and polyetheretherketone (PEEK).

[0104] like Figure 2-Figure 7 As shown, in some embodiments, an air intake hole 110 and an air intake hole 110 are provided on the cylinder wall of the cylinder assembly 10; wherein, a heat insulating member 40 is also provided on the cylinder wall of the cylinder assembly 10, and the heat insulating member 40 is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110.

[0105] The air intake and exhaust of the pump structure are realized by setting the air intake holes 110 and the air intake holes 110 respectively; the heat insulation 40 is set on the cylinder wall to play a heat insulation role, reduce the rise of the suction temperature, and ensure the refrigeration capacity of the compressor. In addition, the heat insulation 40 is set on the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110. This is because the air intake process needs to be insulated to avoid overheating of the refrigerant, resulting in a reduction in the air intake volume and a decrease in the refrigeration capacity. The compression process is an important source of temperature rise. Therefore, the heat insulation 40 is not set in the compression process, so that the heat can be transferred to the pump structure, and the aluminum alloy cylinder assembly 10 is used to quickly dissipate heat to improve the heat dissipation effect.

[0106] It should be noted that the fluid compression direction refers to the rotation direction of the crankshaft 20, which is the clockwise direction in this embodiment.

[0107] It should also be noted that the cylinder assembly 10 has five characteristic angles, namely, the front edge angle of the air intake hole 110, the rear edge angle of the air intake hole 110, the front edge angle of the air intake hole 110, the rear edge angle of the air intake hole 110 and the exhaust start angle. When the rotor rotates to different characteristic angles, it corresponds to different states; among them, Figure 3As shown, the rear edge angle of the suction hole 110 is α, and the suction starts when the rotor rotates clockwise to the rear edge angle α of the suction hole 110; the exhaust starting angle is β, and when the rotor rotates clockwise to the exhaust starting angle β, the exhaust pressure is reached and the exhaust starts;

[0108] In addition, when the rotor starts to rotate from 0° to 2°, the process from the edge angle α behind the intake hole 110 to 2° is the intake process; when the rotor starts the second rotation, that is, the process from the rotor starts to rotate from 2° to 4°, the process from 2° + the front edge angle of the intake hole 110 to 2° + the exhaust starting angle β is the compression process, at which time the pressure rises, and the process from 2° + the exhaust starting angle β to 4° - the rear edge angle of the intake hole 110 is the exhaust process.

[0109] It should also be noted that the heat insulation component can be provided on the entire section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110, or can be provided on only a part of the section.

[0110] In some embodiments, the cutoff angle of the thermal insulation 40 along the fluid compression direction is 200°-340°.

[0111] By setting the cut-off angle to 200°-340° and limiting the interval range of the heat insulating member 40, it is not only ensured that the heat insulating member 40 can be applied to different working conditions of the compressor, but also ensured that the heat insulating member 40 can avoid the area where the air intake hole 110 is located. Because the exhaust angle of the compressor is different under different working conditions, when the cut-off angle is less than 200°, the heat insulating member 40 cannot meet the requirements of different working conditions of the compressor; when the cut-off angle is greater than 340°, the heat insulating member 40 will interfere with the area of ​​the air intake hole 110, resulting in partial obstruction of the air intake hole 110.

[0112] It should be noted that if Figure 2 , Figure 3 As shown, the two sides of the thermal insulation member 40 are respectively a first side and a second side, the first side is the side of the thermal insulation member 40 close to the exhaust starting angle β, and the second side is the side of the thermal insulation member 40 away from the exhaust starting angle β. The cut-off angle of the thermal insulation member 40, that is, when the rotor rotates from the vane 50 along the fluid compression direction to the second side of the thermal insulation member 40, the rotation angle is 200°-340°; in addition, the angle between the second side of the thermal insulation member 40 and the vane 50 is θ, θ is 20°-160°, and when the cut-off angle is 340°, θ is 20°, thereby ensuring that the thermal insulation member 40 can avoid the area where the suction hole 110 is located.

[0113] like Figure 1 , Figure 2As shown, in some embodiments, the cylinder assembly 10 includes a cylinder body 130, an upper flange 140 and a lower flange 150; the upper flange 140 is arranged at one end of the cylinder body 130; the lower flange 150 is arranged at the other end of the cylinder body 130; wherein the crankshaft 20 is rotatably connected to the upper flange 140 and the lower flange 150 respectively, and the intake hole 110, the intake hole 110 and the heat insulation member 40 are all arranged on the cylinder wall of the cylinder body 130.

[0114] It should be noted that the cylinder body 130 , the upper flange 140 and the lower flange 150 are all made of aluminum alloy, and the crankshaft 20 is rotatably connected to the upper flange 140 and the lower flange 150 including but not limited to rolling bearings.

[0115] like Figure 2-Figure 7 As shown, in some embodiments, a groove 1301 is provided inside the cylinder wall of the cylinder body 130 or on the inner surface of the cylinder wall of the cylinder body 130, and the groove 1301 is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the suction hole 110, wherein the thermal insulation member 40 is provided in the groove 1301.

[0116] The groove 1301 is provided to facilitate installation of the heat insulating member 40, and the heat insulating member 40 is used for heat insulation, thereby reducing temperature rise and cooling attenuation.

[0117] It should be noted that the heat insulating member 40 includes but is not limited to cast iron heat insulating members and ceramic heat insulating members. By using cast iron or ceramic as the heat insulating member 40, the good self-lubricating characteristics of cast iron or ceramic are utilized to effectively reduce the friction power consumption between the cylinder wall of the cylinder body 130 and the roller 30.

[0118] It should also be noted that, in some embodiments, the inner side surface of the cylinder wall of the cylinder body 130 can be coated with a thin layer of cast iron or ceramic as a thermal insulation member 40, which can also provide insulation and reduce temperature rise and cooling attenuation.

[0119] It should also be noted that if Figure 5 , Figure 6 As shown, a groove 1301 is provided inside the cylinder wall of the cylinder body 130, and the groove 1301 is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the suction hole 110, and the heat insulation member 40 is arranged in the groove 1301; Figure 2 , Figure 3 As shown, a groove 1301 is provided on the inner surface of the cylinder wall of the cylinder body 130, and the groove 1301 is located in the section from the exhaust start angle along the fluid compression direction to the rear edge angle of the suction hole 110, and the heat insulation member 40 is arranged in the groove 1301. It can be understood that the shapes of the groove 1301 arranged inside the cylinder wall and the groove 1301 arranged on the inner surface of the cylinder wall can be different, such as Figure 2 , Figure 6 As shown, the groove 1301 arranged on the inner surface of the cylinder wall includes an arcuate groove segment and straight groove segments respectively located on both sides of the arcuate groove segment, and the groove 1301 arranged inside the cylinder wall only includes the arcuate groove segment.

[0120] It should also be noted that the heat insulating member 40 is adapted to the shape of the groove 1301; it can be understood that when the shape of the groove 1301 provided inside the cylinder wall and the shape of the groove 1301 provided on the inner surface of the cylinder wall are different, the shape of the heat insulating member 40 matching the shape is different; Figure 4 , Figure 7 As shown, the heat insulating member 40 disposed on the inner surface of the cylinder wall includes an arc-shaped heat insulating segment and straight heat insulating segments respectively located on both sides of the arc-shaped heat insulating segment, and the heat insulating member 40 disposed inside the cylinder wall only includes the arc-shaped heat insulating segment.

[0121] In some embodiments, the thickness of the thermal insulation 40 is 2 mm.

[0122] By setting the thickness of the heat insulating member 40 to 2 mm, it is possible to avoid the heat insulating member 40 being too thin, which would result in failure to provide heat insulating effect, and to avoid the heat insulating member 40 being too thick, which would affect the performance of the cylinder assembly 10 .

[0123] Embodiment 5

[0124] like Figure 1 As shown, an embodiment of the present invention provides a pump body structure, including a cylinder assembly 10, a crankshaft 20 and a roller 30; the crankshaft 20 is rotatably arranged in the cylinder assembly 10; the roller 30 is arranged on the crankshaft 20 and is located in the cylinder assembly 10, and the roller 30 rolls along the cylinder wall of the cylinder assembly 10 under the drive of the crankshaft 20, and contacts with the cylinder wall of the cylinder assembly 10 to jointly form a working chamber; wherein, the cylinder assembly 10, the crankshaft 20, and the roller 30 are all made of lightweight materials with a density less than that of the iron-based alloy, and the absolute value of the difference in linear expansion coefficients of any two of the cylinder assembly 10, the crankshaft 20, and the roller 30 is not greater than the preset difference, so that the preset gap between the cylinder assembly 10, the crankshaft 20, and the roller 30 remains stable.

[0125] As can be seen from the above, by using lightweight materials with a density lower than that of iron-based alloys to make the cylinder assembly 10, crankshaft 20, and roller 30, the weight reduction effect is achieved, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor; at the same time, the weight reduction of the roller 30 and the crankshaft 20 is not only beneficial to the shaft balance of the pump body structure, but also can improve vibration noise and enhance the stability of the compressor. By setting the absolute value of the difference between the linear expansion coefficients of any two of the cylinder assembly 10, crankshaft 20, and roller 30 to be no greater than the preset difference, the linear expansion coefficients of the cylinder assembly 10, crankshaft 20, and roller 30 are kept consistent, and the problem of changes in the preset clearance of the friction pair between the cylinder assembly 10, crankshaft 20, and roller 30 due to inconsistent linear expansion coefficients is solved, resulting in increased friction and wear, and even jamming and leakage, thereby ensuring the stability of the preset clearance.

[0126] It should be noted that the crankshaft 20 can rotate under the drive of the motor 4, thereby driving the roller 30 to rotate; an eccentric portion is provided on the crankshaft 20, and the roller 30 is provided on the eccentric portion; the crankshaft 20 drives the rotor to rotate, so that the volume in the working chamber changes periodically, completing the intake and exhaust and compression processes, wherein the shape of the working chamber is crescent-shaped.

[0127] It should also be noted that iron-based materials are materials with iron as the main component, and iron-based materials include iron-based alloys, such as cast iron and steel.

[0128] It should also be noted that the number of the roller 30 may be one or more, and the plurality of rollers 30 are arranged at intervals along the axial direction of the crankshaft 20 .

[0129] In some embodiments, the lightweight material is aluminum alloy, and the cylinder assembly 10, the crankshaft 20 and the roller 30 are all made of aluminum alloy.

[0130] By using aluminum alloy materials to prepare the cylinder assembly 10 and the crankshaft 20, on the one hand, the lightweight and weight-reducing effect of aluminum alloy can be fully utilized, thereby reducing the weight of the pump body structure and achieving lightweight compressor. On the other hand, the heat transfer and heat dissipation advantages of aluminum alloy materials are utilized to reduce the temperature rise during the compression process and improve the compression efficiency.

[0131] It should be noted that aluminum alloys are divided into two categories according to the molding method, namely, deformed aluminum and die-cast aluminum; the cylinder assembly 10, the roller 30, the crankshaft 20 and the vane 50 can be made of deformed aluminum or die-cast aluminum, and the types of aluminum alloys used by the cylinder assembly 10, the roller 30, the crankshaft 20 and the vane 50 can be the same or different, and the selection is made according to actual needs, and this application does not make specific restrictions. For example, the crankshaft 20 can be made of deformed aluminum 4032, which has higher strength than cast aluminum; the upper flange 140 and the lower flange 150 are made of cast aluminum YL113, which has fast molding and high utilization rate; the roller 30 and the vane 50 are made of 7 series super-hard aluminum alloy 7075.

[0132] In some embodiments, the lightweight material is aluminum alloy or polymer; wherein the cylinder assembly 10 and the crankshaft 20 are both made of aluminum alloy, and the roller 30 is made of polymer, and the density of the roller 30 is less than that of the aluminum alloy.

[0133] By using aluminum alloy materials to prepare the cylinder assembly 10, the crankshaft 20 and the roller 30, on the one hand, the lightweight effect of aluminum alloy is fully utilized, thereby reducing the weight of the pump body structure and realizing lightweighting of the compressor, and on the other hand, the heat transfer and heat dissipation advantages of aluminum alloy materials are utilized to reduce the temperature rise during the compression process and improve the compression efficiency. By using polymers to prepare the roller 30, the roller 30 can meet the lightweight design while keeping the linear expansion coefficient of the roller 30 consistent with the linear expansion coefficient of the cylinder assembly 10 and the crankshaft 20, thereby avoiding problems such as wear, jamming, and leakage caused by excessive differences in linear expansion coefficients, and ensuring the stability of the preset gap.

[0134] It should be noted that the polymer includes but is not limited to polyethersulfone (PES), polyimide (PI), and polyetheretherketone (PEEK).

[0135] like Figure 2-Figure 7 As shown, in some embodiments, an air intake hole 110 and an air intake hole 110 are provided on the cylinder wall of the cylinder assembly 10; wherein, a heat insulating member 40 is also provided on the cylinder wall of the cylinder assembly 10, and the heat insulating member 40 is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110.

[0136] The air intake and exhaust of the pump structure are realized by setting the air intake holes 110 and the air intake holes 110 respectively; the heat insulation 40 is set on the cylinder wall to play a heat insulation role, reduce the rise of the suction temperature, and ensure the refrigeration capacity of the compressor. In addition, the heat insulation 40 is set on the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110. This is because the air intake process needs to be insulated to avoid overheating of the refrigerant, resulting in a reduction in the air intake volume and a decrease in the refrigeration capacity. The compression process is an important source of temperature rise. Therefore, the heat insulation 40 is not set in the compression process, so that the heat can be transferred to the pump structure, and the aluminum alloy cylinder assembly 10 is used to quickly dissipate heat to improve the heat dissipation effect.

[0137] It should be noted that the fluid compression direction refers to the rotation direction of the crankshaft 20, which is the clockwise direction in this embodiment.

[0138] It should also be noted that the cylinder assembly 10 has five characteristic angles, namely, the front edge angle of the air intake hole 110, the rear edge angle of the air intake hole 110, the front edge angle of the air intake hole 110, the rear edge angle of the air intake hole 110 and the exhaust start angle. When the rotor rotates to different characteristic angles, it corresponds to different states; among them, Figure 3As shown, the rear edge angle of the suction hole 110 is α, and the suction starts when the rotor rotates clockwise to the rear edge angle α of the suction hole 110; the exhaust starting angle is β, and when the rotor rotates clockwise to the exhaust starting angle β, the exhaust pressure is reached and the exhaust starts;

[0139] In addition, when the rotor starts to rotate from 0° to 2°, the process from the edge angle α behind the intake hole 110 to 2° is the intake process; when the rotor starts the second rotation, that is, the process from the rotor starts to rotate from 2° to 4°, the process from 2° + the front edge angle of the intake hole 110 to 2° + the exhaust starting angle β is the compression process, at which time the pressure rises, and the process from 2° + the exhaust starting angle β to 4° - the rear edge angle of the intake hole 110 is the exhaust process.

[0140] It should also be noted that the heat insulation component can be provided on the entire section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole 110, or can be provided on only a part of the section.

[0141] In some embodiments, the cutoff angle of the thermal insulation 40 along the fluid compression direction is 200°-340°.

[0142] By setting the cut-off angle to 200°-340° and limiting the interval range of the heat insulating member 40, it is not only ensured that the heat insulating member 40 can be applied to different working conditions of the compressor, but also ensured that the heat insulating member 40 can avoid the area where the air intake hole 110 is located. Because the exhaust angle of the compressor is different under different working conditions, when the cut-off angle is less than 200°, the heat insulating member 40 cannot meet the requirements of different working conditions of the compressor; when the cut-off angle is greater than 340°, the heat insulating member 40 will interfere with the area of ​​the air intake hole 110, resulting in partial obstruction of the air intake hole 110.

[0143] It should be noted that if Figure 2 , Figure 3 As shown, the two sides of the thermal insulation member 40 are respectively a first side and a second side, the first side is the side of the thermal insulation member 40 close to the exhaust starting angle β, and the second side is the side of the thermal insulation member 40 away from the exhaust starting angle β. The cut-off angle of the thermal insulation member 40, that is, when the rotor rotates from the vane 50 along the fluid compression direction to the second side of the thermal insulation member 40, the rotation angle is 200°-340°; in addition, the angle between the second side of the thermal insulation member 40 and the vane 50 is θ, θ is 20°-160°, and when the cut-off angle is 340°, θ is 20°, thereby ensuring that the thermal insulation member 40 can avoid the area where the suction hole 110 is located.

[0144] like Figure 1 , Figure 2As shown, in some embodiments, the cylinder assembly 10 includes a cylinder body 130, an upper flange 140 and a lower flange 150; the upper flange 140 is arranged at one end of the cylinder body 130; the lower flange 150 is arranged at the other end of the cylinder body 130; wherein the crankshaft 20 is rotatably connected to the upper flange 140 and the lower flange 150 respectively, and the intake hole 110, the intake hole 110 and the heat insulation member 40 are all arranged on the cylinder wall of the cylinder body 130.

[0145] It should be noted that the cylinder body 130 , the upper flange 140 and the lower flange 150 are all made of aluminum alloy, and the crankshaft 20 is rotatably connected to the upper flange 140 and the lower flange 150 including but not limited to rolling bearings.

[0146] like Figure 2-Figure 7 As shown, in some embodiments, a groove 1301 is provided inside the cylinder wall of the cylinder body 130 or on the inner surface of the cylinder wall of the cylinder body 130, and the groove 1301 is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the suction hole 110, wherein the thermal insulation member 40 is provided in the groove 1301.

[0147] The groove 1301 is provided to facilitate installation of the heat insulating member 40, and the heat insulating member 40 is used for heat insulation, thereby reducing temperature rise and cooling attenuation.

[0148] It should be noted that the heat insulating member 40 includes but is not limited to cast iron heat insulating members and ceramic heat insulating members. By using cast iron or ceramic as the heat insulating member 40, the good self-lubricating characteristics of cast iron or ceramic are utilized to effectively reduce the friction power consumption between the cylinder wall of the cylinder body 130 and the roller 30.

[0149] It should also be noted that, in some embodiments, the inner side surface of the cylinder wall of the cylinder body 130 can be coated with a thin layer of cast iron or ceramic as a thermal insulation member 40, which can also provide insulation and reduce temperature rise and cooling attenuation.

[0150] It should also be noted that if Figure 5 , Figure 6 As shown, a groove 1301 is provided inside the cylinder wall of the cylinder body 130, and the groove 1301 is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the suction hole 110, and the heat insulation member 40 is arranged in the groove 1301; Figure 2 , Figure 3 As shown, a groove 1301 is provided on the inner surface of the cylinder wall of the cylinder body 130, and the groove 1301 is located in the section from the exhaust start angle along the fluid compression direction to the rear edge angle of the suction hole 110, and the heat insulation member 40 is arranged in the groove 1301. It can be understood that the shapes of the groove 1301 arranged inside the cylinder wall and the groove 1301 arranged on the inner surface of the cylinder wall can be different, such as Figure 2 , Figure 6 As shown, the groove 1301 arranged on the inner surface of the cylinder wall includes an arcuate groove segment and straight groove segments respectively located on both sides of the arcuate groove segment, and the groove 1301 arranged inside the cylinder wall only includes the arcuate groove segment.

[0151] It should also be noted that the heat insulating member 40 is adapted to the shape of the groove 1301; it can be understood that when the shape of the groove 1301 provided inside the cylinder wall and the shape of the groove 1301 provided on the inner surface of the cylinder wall are different, the shape of the heat insulating member 40 matching the shape is different; Figure 4 , Figure 7 As shown, the heat insulating member 40 disposed on the inner surface of the cylinder wall includes an arc-shaped heat insulating segment and straight heat insulating segments respectively located on both sides of the arc-shaped heat insulating segment, and the heat insulating member 40 disposed inside the cylinder wall only includes the arc-shaped heat insulating segment.

[0152] In some embodiments, the thickness of the thermal insulation 40 is 2 mm.

[0153] By setting the thickness of the heat insulating member 40 to 2 mm, it is possible to avoid the heat insulating member 40 being too thin, which would result in failure to provide heat insulating effect, and to avoid the heat insulating member 40 being too thick, which would affect the performance of the cylinder assembly 10 .

[0154] like Figure 8 As shown, in some embodiments, the roller 30 is a hollow structure.

[0155] By setting the roller 30 as a hollow structure, on the one hand, it plays an insulating role and reduces the heat transfer between the compression chamber and the suction chamber; on the other hand, it reduces the mass of the roller 30, optimizes the unbalanced force on the crankshaft 20 during the rotation of the rotor, and improves vibration and noise.

[0156] like Figure 2 As shown, in some embodiments, the pump body structure also includes a slide 50, which is movably disposed on the cylinder assembly 10, and the slide 50 is always in contact with the roller 30 to separate the working chamber into an intake chamber and a compression chamber; wherein the intake holes 110 and the intake holes 110 are respectively located on both sides of the slide 50.

[0157] It should be noted that the cylinder body 130 is provided with a cylinder hole 1303 which passes through the cylinder body 130 in the axial direction, and the inner surface of the cylinder wall of the cylinder body 130 is provided with a slide groove 1302, and the slide 50 is movably arranged in the slide groove 1302; in addition, the pump body structure also includes a spring arranged in the slide groove 1302, so that the slide 50 and the roller 30 are always kept in contact with each other through the spring.

[0158] like Fig. 9 As shown, in some embodiments, the sliding vane 50 is a ceramic sliding vane, or the sliding vane 50 is an aluminum alloy sliding vane and the sliding vane 50 is a hollow structure.

[0159] The ceramic sliding vane 50 or the hollow aluminum alloy sliding vane 50 is provided to provide insulation and reduce heat transfer between the compression chamber and the suction chamber.

[0160] It should be noted that, in some embodiments, at least one contact surface of the friction pair in the pump body structure is subjected to friction reduction and wear resistance treatment, wherein the friction reduction and wear resistance treatment includes but is not limited to one or more of micro-arc oxidation, (hard) anodizing, chemical nickel-phosphorus plating, surface texturing, nitriding, sulfurizing, carburizing, boronizing, and surface coating; for example, the inner side surface of the cylinder wall and the roller 30 are friction pairs, and the friction reduction and wear resistance treatment can be performed on the inner side surface of the cylinder wall and the surface of the roller 30. This solves the friction and wear problems of aluminum alloy materials, improves surface hardness, enhances wear resistance, reduces friction coefficient, and reduces friction power consumption.

[0161] Embodiment 6

[0162] like Fig.10 As shown, an embodiment of the present invention further provides a compressor, comprising a shell 2 and a pump body structure 1 of any embodiment of the present invention, wherein the pump body structure 1 is arranged in the shell 2, and thus has all the technical effects brought by the technical solutions of the above embodiments.

[0163] It should be noted that the compressor further includes a motor 4 disposed in the housing 2 and a liquid reservoir 3 disposed on the outer wall of the housing 2 . The rotating shaft of the motor 4 is connected to the crankshaft 20 , and the liquid reservoir 3 is connected to the air intake hole 110 .

[0164] It should also be noted that the pump body structure 1 can be connected to the inner wall of the shell 2 by welding, for example, by welding the upper flange 140 to the inner wall of the shell 2, or by welding the cylinder body 130 to the inner wall of the shell 2.

[0165] In some embodiments, the housing 2 is made of aluminum alloy.

[0166] By providing the aluminum alloy housing 2, the heat dissipation advantage of the aluminum alloy is fully utilized, heat accumulation is avoided, and the temperature rise during the compression process is effectively reduced, thereby improving the compression efficiency.

[0167] It should be noted that the housing 2 includes a main body and an upper cover and a lower cover respectively disposed at two ends of the main body.

[0168] It should also be noted that aluminum alloys are divided into two categories according to the molding method, namely, deformed aluminum and die-cast aluminum; the housing 2 can be made of deformed aluminum or die-cast aluminum, and the type of aluminum alloy used by the housing 2 and the pump body structure 1 can be the same or different, depending on actual needs, and this application does not impose specific restrictions. For example, the housing is made of deformed aluminum 6061, which has excellent weldability, processability, and high strength.

[0169] In some embodiments, the refrigerant used by the compressor is R290 or R32.

[0170] It should be noted that R290 (propane) is a natural hydrocarbon refrigerant that can be directly obtained from liquefied gas; R290 molecules do not contain chlorine atoms, so the ODP (ozone depletion potential) is zero and has no destructive effect on the ozone layer. In addition, compared with HFC (hydrofluorocarbon) substances, the GWP (global warming potential) of R290 is close to 0, and it has almost no effect on the greenhouse effect.

[0171] It should also be noted that R32 (dichloromethane) has the advantages of high efficiency and energy saving, environmental protection and low carbon, good safety and high energy efficiency.

[0172] It should also be noted that, preferably, the refrigerant used in the compressor is R290;

[0173] The compressor of the present invention can be applied to different application scenarios and refrigerant requirements, and is particularly suitable for refrigerant scenarios such as R290. A stress simulation was performed for the solution of the present invention, wherein: Fig.11 This is a stress simulation diagram of the compressor of the present invention when it is applied to the R32 refrigerant scenario. Fig.12 This is a stress simulation diagram of the compressor of the present invention when it is applied to the R290 refrigerant scenario. By comparing Fig.11 and Fig.12 When it is used in R32 refrigerant scenarios, the maximum contact stress of the shaft system is reduced from 49.9MPa to 25.2MPa when it is used in R290 refrigerant scenarios. This not only meets the design requirement of 35.4MPa, but also effectively avoids contact wear and improves shaft system reliability.

[0174] In addition, the maximum contact stress of the shaft system refers to the contact stress between the crankshaft 20 and the upper flange 140 and the lower flange 150, because the crankshaft 20 is supported by the upper flange 140 and the lower flange 150, for example. Figure 1 As shown, the crankshaft 20 is sleeved in the through holes of the upper flange 140 and the lower flange 150, and a clearance fit is adopted. A fixed lubrication gap is preset, and relative sliding is performed therebetween. Under the action of centrifugal force, gas force, etc., on the one hand, the crankshaft 20 produces flexural deformation, and on the other hand, the crankshaft 20 deviates from the axial position and runs along its trajectory (due to the existence of the lubrication gap), so the crankshaft 20 will come into contact with the hole wall of the upper flange 140 and the hole wall of the lower flange 150.

[0175] Embodiment 7

[0176] An embodiment of the present invention further provides a refrigeration device, including a compressor according to any embodiment of the present invention, and thus having all the technical effects brought about by the technical solutions of the above embodiments.

[0177] Although the present invention has been described with reference to preferred embodiments, various modifications may be made thereto and parts thereof may be replaced by equivalents without departing from the scope of the present invention. In particular, the various technical features mentioned in the various embodiments may be combined in any manner as long as there are no structural conflicts. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A pump body structure, characterized in that: include: Cylinder assembly; A crankshaft rotatably inserted into the cylinder assembly; as well as A roller, arranged on the crankshaft and located in the cylinder assembly, wherein the roller rolls along the cylinder wall of the cylinder assembly under the drive of the crankshaft and contacts the cylinder wall of the cylinder assembly to form a working chamber together; Among them, the cylinder assembly, the crankshaft, and the roller are all made of lightweight materials with a density lower than that of iron-based alloys, and the absolute value of the difference in linear expansion coefficients of any two of the cylinder assembly, the crankshaft, and the roller is not greater than a preset difference, so that the preset gap between the cylinder assembly, the crankshaft, and the roller remains stable.

2. The pump body structure according to claim 1, characterized in that: The lightweight material is aluminum alloy, and the cylinder assembly, the crankshaft and the roller are all made of aluminum alloy.

3. The pump body structure according to claim 1, characterized in that: The lightweight material is aluminum alloy or polymer; wherein the cylinder assembly and the crankshaft are both made of aluminum alloy, and the roller is made of polymer, and the density of the roller is less than that of the aluminum alloy.

4. The pump body structure according to any one of claims 1 to 3, characterized in that: The cylinder wall of the cylinder assembly is provided with an air intake hole and an air exhaust hole; wherein, the cylinder wall of the cylinder assembly is also provided with a heat insulating member, and the heat insulating member is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the air intake hole.

5. The pump structure according to claim 4, characterized in that: Along the fluid compression direction, the cut-off angle of the thermal insulation element is 200°-340°.

6. The pump structure according to claim 4, characterized in that: The cylinder assembly comprises: Cylinder body; an upper flange, disposed at one end of the cylinder body; and A lower flange is arranged at the other end of the cylinder body; Wherein, the crankshaft is rotatably connected to the upper flange and the lower flange respectively, and the air intake hole, the air exhaust hole and the heat insulation component are all arranged on the cylinder wall of the cylinder body.

7. The pump structure according to claim 6, characterized in that: A groove is provided inside the cylinder wall of the cylinder body or on the inner surface of the cylinder wall of the cylinder body, and the groove is located in the section from the exhaust starting angle along the fluid compression direction to the rear edge angle of the suction port, wherein the heat insulation member is provided in the groove.

8. The pump structure according to claim 7, characterized in that: The thickness of the thermal insulation member is 2 mm.

9. The pump structure according to any one of claims 1 to 3, characterized in that: The roller is a hollow structure.

10. The pump structure according to claim 4, characterized in that: The pump body structure also includes a sliding vane, which is movably arranged on the cylinder assembly and is always in contact with the roller to separate the working chamber into an intake chamber and a compression chamber; wherein the intake hole and the exhaust hole are respectively located on both sides of the sliding vane.

11. The pump structure according to claim 10, characterized in that: The sliding vane is a ceramic sliding vane; or the sliding vane is an aluminum alloy sliding vane and has a hollow structure.

12. A compressor, characterized in that: It comprises a shell and a pump body structure as claimed in any one of claims 1 to 11, wherein the pump body structure is arranged in the shell.

13. The compressor according to claim 12, characterized in that The shell is made of aluminum alloy.

14. The compressor according to claim 12, characterized in that The refrigerant used by the compressor is R290 or R32.

15. A refrigeration device, characterized in that: Comprising a compressor as claimed in any one of claims 12-14.

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