Compressor applied to air conditioning system, and air conditioning system

Abstract

A compressor applied to an air conditioning system, and an air conditioning system. The compressor comprises a housing, a motor, and a pump body assembly. The pump body assembly comprises a crankshaft, a fixed scroll, an orbiting scroll, and a bracket. The crankshaft passes through the motor, the fixed scroll, the orbiting scroll, and the bracket. The fixed scroll is provided with a first scroll wrap portion and a first bearing portion, and the first bearing portion is provided with a first bearing hole. The orbiting scroll is provided with a second scroll wrap portion and an eccentric bearing hole. The bracket is provided with a second bearing portion, and the second bearing portion is provided with a second bearing hole. The crankshaft comprises a first shaft section, an eccentric section, and a second shaft section. The outer diameter D1 of the first shaft section satisfies the following relational expression: 11 mm≤D1≤15 mm; the outer diameter D2 of the eccentric section satisfies the following relational expression: 14 mm≤D2≤18 mm; and the outer diameter D3 of the second shaft section satisfies the following relational expression: 9 mm≤D3≤13 mm. The present application can solve the problem in the prior art of the contradiction between the reliability and the energy efficiency of a scroll compressor.

Description

Compressors and air conditioning systems used in air conditioning systems

[0001] This application claims priority to Chinese Patent Application No. 202510103243.6, filed on January 22, 2025, entitled "Compressor and Air Conditioning System for Use in Air Conditioning Systems", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of refrigeration technology, and more specifically, to a compressor and an air conditioning system for use in an air conditioning system. Background Technology

[0003] Air conditioners are high-power appliances, and users are increasingly demanding higher energy efficiency from them. As the core component of an air conditioner, the compressor's energy efficiency has a significant impact on the overall energy efficiency of the air conditioner.

[0004] Existing compressors typically include rolling rotor compressors and scroll compressors. Among them, scroll compressors have higher energy efficiency than rolling rotor compressors due to their higher volumetric efficiency and lower leakage. However, there are often some contradictions in the structural design of scroll compressors, such as the contradiction between compressor energy efficiency and compressor reliability. Furthermore, existing scroll compressors are over-designed to ensure reliability, thus sacrificing performance aspects such as compressor energy efficiency. Summary of the Invention

[0005] The main objective of this application is to provide a compressor and air conditioning system for use in air conditioning systems, so as to solve the problem of the contradiction between the reliability and energy efficiency of scroll compressors in the prior art.

[0006] According to one aspect of this application, a compressor for use in an air conditioning system is provided. The air conditioning system includes a refrigerant, an evaporator, a condenser, a throttling device, and the compressor. The rated cooling capacity CC of the air conditioning system satisfies the relationship: 2500W ≤ CC ≤ 3700W. The compressor includes a vertical variable frequency scroll compressor, and further includes:

[0007] The housing has a receiving cavity, and the bottom of the receiving cavity is provided with an oil storage space for storing lubricating oil;

[0008] An electric motor is disposed within the accommodating cavity, and the electric motor includes a rotor and a stator sleeved on the outer periphery of the rotor;

[0009] A pump body assembly is disposed within the accommodating cavity and near the bottom of the accommodating cavity. The pump body assembly includes a crankshaft, a stationary scroll plate, a moving scroll plate, and a bracket. The crankshaft is rotatably disposed within the accommodating cavity and passes through the motor, the stationary scroll plate, the moving scroll plate, and the bracket. The stationary scroll plate has a first scroll tooth on the side near the moving scroll plate, and the moving scroll plate has a second scroll tooth that meshes with the first scroll tooth. The first scroll tooth and the second scroll tooth mesh to form a compression cavity.

[0010] The crankshaft includes a first shaft section, an eccentric section, and a second shaft section. The first shaft section, the eccentric section, and the second shaft section are arranged sequentially along the axial direction of the crankshaft. The stationary scroll plate has a first bearing portion on the side opposite to the moving scroll plate, and the first bearing portion has a first bearing hole. The moving scroll plate has an eccentric bearing hole through which the eccentric section passes. The bracket has a second bearing portion on the side opposite to the moving scroll plate, and the second bearing portion has a second bearing hole.

[0011] The outer diameter D1 of the first shaft segment satisfies the following relationship: 11mm≤D1≤15mm;

[0012] The outer diameter D2 of the eccentric section satisfies the following relationship: 14mm≤D2≤18mm;

[0013] The outer diameter D3 of the second shaft segment satisfies the following relationship: 9mm≤D3≤13mm.

[0014] Furthermore, the outer diameter D1 of the first shaft segment satisfies the following relationship: 12.5mm ≤ D1 ≤ 13.5mm;

[0015] The outer diameter D3 of the second shaft segment satisfies the following relationship: 9.5mm≤D3≤11.5mm.

[0016] Furthermore, the outer diameter D4 of the stator satisfies the following relationship: 96mm≤D4≤104mm.

[0017] Furthermore, the outer diameter D5 of the moving scroll disk satisfies the following relationship: 78mm≤D5≤82mm.

[0018] Furthermore, the first shaft segment has a first support fitting portion that mates with the first bearing hole or the second bearing hole, and along the axial direction of the crankshaft, the width W1 of the first support fitting portion satisfies the relationship: 22mm ≤ W1 ≤ 35mm; and / or,

[0019] The first shaft segment has a first support fitting portion that mates with the first bearing hole or the second bearing hole. Along the axial direction of the crankshaft, the maximum distance L1 between the end of the first support fitting portion away from the eccentric segment and the end of the eccentric segment near the first shaft segment satisfies the relationship: 30mm≤L1≤45mm.

[0020] Furthermore, the crankshaft is provided with an oil supply channel, which extends from the end of the second shaft segment toward the direction close to the first shaft segment;

[0021] The outer surface of the first support mating part is provided with a first oil groove, the first oil groove is connected to the oil supply channel through a first oil hole, and an annular groove is provided on the first shaft segment. The annular groove is located between the first support mating part and the eccentric segment and is arranged around the circumference of the first shaft segment. The first oil groove extends along the axial direction of the crankshaft and extends from the first support mating part to the annular groove.

[0022] Furthermore, in the projection along the direction from the first shaft segment to the eccentric segment, the projections of both the first shaft segment and the eccentric segment include circles. A first ray is drawn with the center of the first shaft segment as the endpoint and passing through the center of the eccentric segment. The first ray is 0° and counterclockwise is the direction of rotation of the crankshaft and the direction of increasing angle. The first oil groove is disposed on the outer surface of the first shaft segment and is located between 0° and 180° and between 270° and 360°.

[0023] Furthermore, the first support mating part includes two support sections arranged sequentially along the crankshaft axis. The outer surfaces of the two support sections each have the first oil groove. In the two support sections, the width of the support section located closer to the eccentric section along the crankshaft axis is greater than the width of the support section located farther from the eccentric section along the crankshaft axis.

[0024] Furthermore, the outer surface of the first support mating part is provided with a first annular groove, the first annular groove is arranged around the circumference of the first shaft segment, and the first annular groove is located between the two support segments to at least store lubricating oil.

[0025] Furthermore, the eccentric section has a second support fitting part that mates with the eccentric bearing hole. Along the axial direction of the crankshaft, the width W2 of the second support fitting part satisfies the relationship: 12mm≤W2≤18mm.

[0026] Furthermore, the eccentric section has a second support fitting portion that mates with the eccentric bearing hole. The center of the width of the second support fitting portion along the crankshaft axis is located between the end face of the moving scroll disk facing away from the second scroll tooth portion at half the height of the second scroll tooth portion along the crankshaft axis.

[0027] Furthermore, the second shaft segment has a third support fitting portion that mates with the first bearing hole or the second bearing hole. Along the axial direction of the crankshaft, the width W3 of the third support fitting portion satisfies the relationship: 10mm≤W3≤18mm.

[0028] Furthermore, the first shaft segment has a first support fitting portion that mates with the first bearing hole or the second bearing hole, and the outer surface of the first support fitting portion is provided with a first oil groove;

[0029] The eccentric section has a second support fitting part that mates with the eccentric bearing hole. The second support fitting part has a second oil groove. The second oil groove is disposed on the outer surface of the second support fitting part along the axial direction of the crankshaft, and the second oil groove is connected to the first oil groove through an annular groove.

[0030] Furthermore, the crankshaft is provided with an oil supply channel, which extends from the end of the second shaft segment toward the direction close to the first shaft segment;

[0031] The eccentric section has a second support fitting part that mates with the eccentric bearing hole. The second support fitting part has a third oil groove. The third oil groove is located on the outer surface of the second support fitting part and extends along the axial direction of the crankshaft. The width of the third oil groove along the axial direction of the crankshaft is smaller than the width of the second support fitting part along the axial direction of the crankshaft. The third oil groove is connected to the oil supply channel through a second oil hole.

[0032] Furthermore, the second oil groove has a first groove edge and a second groove edge arranged opposite to each other along the circumference of the crankshaft, and the angle between the line connecting the first groove edge and the center of the eccentric segment and the line connecting the second groove edge and the center of the eccentric segment is θ1.

[0033] The third oil groove has a third groove side and a fourth groove side arranged opposite to each other along the circumference of the crankshaft, and the angle between the line connecting the third groove side and the center of the eccentric segment and the line connecting the fourth groove side and the center of the eccentric segment is θ2.

[0034] Among them, θ1 and θ2 satisfy the relationship that θ1+θ2≥30°.

[0035] Furthermore, in the projection along the direction from the first shaft segment to the eccentric segment, the projections of both the first shaft segment and the eccentric segment include circles. A first ray is drawn with the center of the first shaft segment as the endpoint and passing through the center of the eccentric segment. The first ray is 0° and counterclockwise is the direction of rotation of the crankshaft and the direction of increasing angle. The second oil groove and the third oil groove are disposed on the outer surface of the eccentric segment and are located between 90° and 360°.

[0036] Furthermore, the crankshaft is provided with an oil supply channel, which extends from the end of the second shaft segment toward the direction close to the first shaft segment;

[0037] The second shaft segment has a third support fitting part that mates with the first bearing hole or the second bearing hole. The outer surface of the third support fitting part is provided with a fourth oil groove. The fourth oil groove is connected to the oil supply channel through a third oil hole, and the width of the fourth oil groove along the crankshaft axis is smaller than the width of the third support fitting part along the crankshaft axis.

[0038] Furthermore, in the projection along the direction from the first shaft segment to the eccentric segment, the projections of both the first shaft segment and the eccentric segment include circles. Taking the center of the circle of the first shaft segment as the endpoint and passing through the center of the circle of the eccentric segment, a first ray is drawn. Taking the first straight line as 0° and counterclockwise as the direction of rotation and angle increase of the crankshaft, the fourth oil groove is disposed on the outer surface of the second shaft segment and located between 0° and 210° and between 270° and 360°.

[0039] Furthermore, the first shaft segment has a first support fitting portion that mates with the first bearing hole or the second bearing hole, and the outer surface of the first support fitting portion is provided with a first oil groove;

[0040] The eccentric section has a second support fitting part that mates with the eccentric bearing hole, and the outer surface of the second support fitting part is provided with a second oil groove and a third oil groove.

[0041] The second shaft segment has a third support fitting part that mates with the first bearing hole or the second bearing hole, and the outer surface of the third support fitting part is provided with a fourth oil groove;

[0042] The first oil tank, the second oil tank, the third oil tank, and the fourth oil tank all include straight or spiral oil tanks, and the cross-sectional area of ​​each of the first oil tank, the second oil tank, the third oil tank, and the fourth oil tank is greater than or equal to 0.35 mm. 2 .

[0043] Furthermore, a first fitting clearance exists between the first shaft segment and the first bearing bore or the second bearing bore, and the width A1 of the first fitting clearance along the radial direction of the crankshaft satisfies the relationship: 0.015mm ≤ A1 ≤ 0.04mm; and / or,

[0044] A second fitting clearance exists between the eccentric section and the eccentric bearing bore. Along the radial direction of the crankshaft, the width A2 of the second fitting clearance satisfies the following relationship: 0.015mm ≤ A2 ≤ 0.04mm; and / or,

[0045] The second shaft segment has a third fitting clearance with the first bearing hole or the second bearing hole. Along the radial direction of the crankshaft, the width A3 of the third fitting clearance satisfies the relationship: 0.015mm≤A3≤0.04mm.

[0046] Furthermore, the first shaft segment has a first support fitting portion that mates with the first bearing hole or the second bearing hole, and the outer diameter of the first support fitting portion gradually decreases along the direction away from the eccentric segment.

[0047] Furthermore, the taper C of the first support fitting part satisfies the relationship: C = H1 / L2, and 1 / 2000 ≤ C ≤ 1 / 1000, where H1 is the maximum distance between the first support fitting part and the inner wall of the first bearing hole or the second bearing hole, and L2 is the height of the first support fitting part along the crankshaft axis.

[0048] Furthermore, a bushing is provided between the eccentric bearing hole of the moving scroll disk and the crankshaft.

[0049] Furthermore, the bushing is made of at least one of polytetrafluoroethylene, carbon, and aluminum alloy materials.

[0050] Furthermore, a second annular groove is provided on the side of the stationary vortex disk or the support near the eccentric section. The second annular groove is arranged around the outer periphery of the first bearing hole along the circumference of the stationary vortex disk or around the outer periphery of the second bearing hole along the circumference of the support, and is spaced apart from the first bearing hole or the second bearing hole.

[0051] Furthermore, along the radial direction of the crankshaft, the minimum thickness T1 between the side of the second annular groove near the first bearing hole and the first bearing hole, or between the side of the second annular groove near the second bearing hole and the second bearing hole, satisfies the relationship: T1 ≥ 1.5 mm; and / or,

[0052] Along the radial direction of the crankshaft, the width D6 of the second annular groove satisfies the relationship: 1.5mm ≤ D6 ≤ 2.5mm; and / or,

[0053] Along the axial direction of the crankshaft, the height H2 of the second annular groove satisfies the following relationship: 4mm≤H2≤7mm.

[0054] Furthermore, the minimum thickness T2 between the side of the second vortex tooth located near the eccentric bearing hole and the eccentric bearing hole satisfies the relationship: T2≥1.5mm.

[0055] Furthermore, along the direction away from the eccentric segment, the cross-sectional area of ​​the first bearing portion gradually decreases, and the minimum thickness T3 of the first bearing portion on the side away from the eccentric segment satisfies the relationship: T3≥1.5mm.

[0056] Furthermore, a thrust surface is provided at one end of the eccentric segment near the second shaft segment or at one end of the second shaft segment away from the eccentric segment.

[0057] Furthermore, the cross-sectional area S of the thrust surface satisfies the following relationship: 45mm 2 ≤S≤85mm 2 .

[0058] Furthermore, the crankshaft comprises a ductile iron crankshaft, wherein the tensile strength of the ductile iron crankshaft is greater than or equal to 500 MPa; and / or,

[0059] The outer surface of the crankshaft is treated with phosphating or a combination of phosphating and molybdenum treatment or a diamond-like carbon film treatment; and / or,

[0060] The crankshaft comprises a low-carbon steel crankshaft, wherein the carbon content of the low-carbon steel crankshaft is less than or equal to 0.6%; and / or,

[0061] The surface hardness of the crankshaft is greater than or equal to 45 HRC.

[0062] Furthermore, when the temperature of the lubricating oil is 40°C, the kinematic viscosity γ of the lubricating oil satisfies the following relationship: 50 mm 2 / s≤γ≤80mm 2 / s; and / or,

[0063] The amount of lubricating oil injected, G, satisfies the following relationship: 200mL≤G≤350mL.

[0064] Furthermore, the compressor also includes a liquid receiver, and the housing has an air inlet and an air outlet. The air inlet is connected to the liquid receiver and the compression chamber, and the air outlet is connected to the accommodating chamber and the outside.

[0065] The liquid storage volume V of the liquid reservoir satisfies the relationship 300mL≤V≤500mL.

[0066] On the other hand, this application also provides an air conditioning system, which includes the compressor described above for use in air conditioning systems.

[0067] In this application, during the actual manufacturing of the compressor, both the motor and pump assembly can be installed within the housing cavity, with the crankshaft passing through the motor, stationary scroll, moving scroll, and support. The motor is driven by the crankshaft; when the motor drives the crankshaft to rotate, it drives the eccentric section to rotate, thereby causing the moving scroll to rotate synchronously. This, in turn, causes the stationary scroll to rotate relative to the moving scroll, compressing the refrigerant entering the compression chamber and effectively improving the compressor's energy efficiency. Simultaneously, by setting the outer diameter D1 of the first shaft section, the outer diameter D2 of the eccentric section, and the outer diameter D3 of the second shaft section, this application can effectively ensure the compressor's reliability and maintain optimal energy efficiency in air conditioning systems with a cooling capacity ranging from 2500W to 3700W. Attached Figure Description

[0068] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings:

[0069] Figure 1 is a cross-sectional view of the compressor disclosed in an embodiment of this application;

[0070] Figure 2 is a cross-sectional view of the pump body assembly disclosed in an embodiment of this application;

[0071] Figure 3 is an enlarged view of region A in Figure 2 of the embodiments disclosed in this application;

[0072] Figure 4 is a schematic diagram of the structure of the moving vortex disk disclosed in the embodiment of this application;

[0073] Figure 5 is a cross-sectional view of the moving vortex disk disclosed in the embodiment of this application;

[0074] Figure 6 is a schematic diagram of the static vortex disk disclosed in the embodiment of this application from a first-view perspective;

[0075] Figure 7 is a schematic diagram of the static vortex disk disclosed in the embodiment of this application from a second perspective;

[0076] Figure 8 is a cross-sectional view of the static vortex disk disclosed in the embodiment of this application;

[0077] Figure 9 is a schematic diagram of the structure of the stent disclosed in the embodiment of this application;

[0078] Figure 10 is a cross-sectional view of the bracket disclosed in an embodiment of this application;

[0079] Figure 11 is a cross-sectional view of the crankshaft disclosed in an embodiment of this application;

[0080] Figure 12 is a structural schematic diagram of the crankshaft disclosed in the embodiment of this application from a first-view perspective;

[0081] Figure 13 is a cross-sectional view of SS in Figure 12 of the embodiment disclosed in this application;

[0082] Figure 14 is a structural schematic diagram of the crankshaft disclosed in the embodiment of this application from a second perspective;

[0083] Figure 15 is a cross-sectional view of MM in Figure 14 of the embodiment disclosed in this application;

[0084] Figure 16 is a structural schematic diagram showing the specific location of the first oil tank disclosed in the embodiment of this application;

[0085] Figure 17 is a structural schematic diagram showing the specific locations of the second and third oil tanks disclosed in the embodiments of this application;

[0086] Figure 18 is a structural schematic diagram showing the specific location of the fourth oil tank disclosed in the embodiment of this application;

[0087] Figure 19 is a schematic diagram of a crankshaft with a linear oil groove disclosed in an embodiment of this application;

[0088] Figure 20 is a schematic diagram of a crankshaft with a spiral oil groove disclosed in an embodiment of this application;

[0089] Figure 21 is a schematic diagram of the structure with a thrust surface provided on the eccentric segment disclosed in the embodiment of this application;

[0090] Figure 22 is a schematic diagram of the structure of the second shaft segment with a thrust surface disclosed in the embodiment of this application;

[0091] Figure 23 is a cross-sectional view of a pump body assembly with a bushing disclosed in an embodiment of this application;

[0092] Figure 24 is an enlarged view of region B in Figure 23 of the embodiments disclosed in this application;

[0093] Figure 25 is a cross-sectional view of a stationary vortex disk with a second annular groove disclosed in an embodiment of this application.

[0094] The above-mentioned figures include the following reference numerals: 10, housing; 101, accommodating cavity; 102, oil storage space; 11, air inlet; 12, air outlet; 20, motor; 21, rotor; 22, stator; 30, pump body assembly; 301, compression chamber; 31, crankshaft; 311, first shaft section; 312, eccentric section; 313, second shaft section; 314, oil supply channel; 315, thrust surface; 32, stationary scroll plate; 321, first scroll tooth; 322, first bearing section; 323, first bearing hole; 324, second annular groove; 325, annular groove; 33, moving scroll plate; 331, second scroll tooth; 332, eccentric bearing hole; 34, bracket; 341, second bearing section; 342, second bearing hole; 35, cross slip ring; 40. First support mating part; 41. First oil groove; 42. First oil hole; 43. Support section; 45. First annular groove; 50. First ray; 60. Second support mating part; 61. Second oil groove; 611. First groove edge; 612. Second groove edge; 62. Third oil groove; 621. Third groove edge; 622. Fourth groove edge; 63. Second oil hole; 70. Third support mating part; 71. Fourth oil groove; 72. Third oil hole; 80. Bushing; 90. Liquid reservoir; 100. Straight oil groove; 110. Spiral oil groove. Detailed Implementation

[0095] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0096] 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.

[0097] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0098] As mentioned in the background section, there is a trade-off between the energy efficiency and reliability of existing scroll compressors. Scroll compressors are often over-designed to ensure reliability, thus sacrificing performance such as energy efficiency. To address this, the inventors of this application have designed a novel compressor that resolves the conflict between reliability and energy efficiency in existing scroll compressors. The compressor described in detail below, with reference to the accompanying drawings, will be explained in detail.

[0099] Referring to Figures 1 to 25, according to an embodiment of this application, a compressor for use in an air conditioning system is provided. The air conditioning system includes a refrigerant, an evaporator, a condenser, a throttling device, and a compressor. The rated cooling capacity CC of the air conditioning system satisfies the relationship: 2500W ≤ CC ≤ 3700W. The compressor includes a vertical variable frequency scroll compressor, and further includes a casing 10, a motor 20, and a pump assembly 30. Exemplarily, CC in this embodiment can be set to 2500W, 2600W, 2700W, 2800W, 2900W, 3000W, 3100W, 3200W, 3300W, 3400W, 3500W, 3600W, 3700W, etc.

[0100] Specifically, referring to Figures 1 and 2, the housing 10 has a receiving cavity 101, and the bottom of the receiving cavity 101 is provided with an oil storage space 102 for storing lubricating oil; the motor 20 is disposed in the receiving cavity 101, and the motor 20 includes a rotor 21 and a stator 22 sleeved on the outer periphery of the rotor 21; the pump body assembly 30 is disposed in the receiving cavity 101 and is disposed near the bottom of the receiving cavity 101, and the pump body assembly 30 includes a crankshaft 31, a stationary scroll plate 32, and a moving scroll plate. The crankshaft 31 is rotatably disposed in the accommodating cavity 101, and passes through the motor 20, the stationary scroll 32, the moving scroll 33 and the bracket 34. The stationary scroll 32 is provided with a first scroll tooth 321 on the side near the moving scroll 33, and the moving scroll 33 is provided with a second scroll tooth 331 that meshes with the first scroll tooth 321. The first scroll tooth 321 and the second scroll tooth 331 mesh to form a compression cavity 301.

[0101] The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. The first shaft section 311, the eccentric section 312, and the second shaft section 313 are arranged sequentially along the axial direction of the crankshaft 31. A first bearing portion 322 is provided on the side of the stationary scroll plate 32 away from the moving scroll plate 33. The first bearing portion 322 has a first bearing hole 323. The moving scroll plate 33 has an eccentric bearing hole 332 through which the eccentric section 312 passes. A second bearing portion 341 is provided on the side of the bracket 34 away from the moving scroll plate 33. The second bearing portion 341 has a second bearing hole 342. The outer diameter D1 of the first shaft section 311 satisfies the relationship: 11mm ≤ D1 ≤ 15mm. For example, D1 can be set to 11mm. The outer diameters of the eccentric section 312 are m, 11.5mm, 12mm, 12.5mm, 13mm, 13.5mm, 14mm, 14.5mm, 15mm, etc.; the outer diameter D2 of the eccentric section 312 satisfies the relationship: 14mm≤D2≤18mm, for example, D2 can be set to 14mm, 14.5mm, 15mm, 15.5mm, 16mm, 16.5mm, 17mm, 17.5mm, 18mm, etc.; the outer diameter D3 of the second shaft section 313 satisfies the relationship: 9mm≤D3≤13mm, for example, D3 can be set to 9mm, 9.5mm, 10mm, 10.5mm, 11mm, 11.5mm, 12mm, 12.5mm, 13mm, etc.

[0102] In this embodiment, during the actual manufacturing of the compressor, the motor 20 and the pump assembly 30 can both be installed within the accommodating cavity 101, with the crankshaft 31 passing through the motor 20, the stationary scroll plate 32, the moving scroll plate 33, and the bracket 34. The motor 20 is driven by the crankshaft 31. When the motor 20 drives the crankshaft 31 to rotate, it drives the eccentric section 312 to rotate, thereby causing the moving scroll plate 33 to rotate synchronously. This, in turn, causes the stationary scroll plate 32 to rotate relative to the moving scroll plate 33, compressing the refrigerant entering the compression cavity 301 and effectively improving the compressor's energy efficiency.

[0103] Meanwhile, by setting the outer diameter D1 of the first shaft section 311, the outer diameter D2 of the eccentric section 312, and the outer diameter D3 of the second shaft section 313, this application can effectively ensure the reliability of the compressor in air conditioning systems with a cooling capacity in the range of 2500W to 3700W, while also ensuring that the energy efficiency of the compressor is at a relatively high level.

[0104] Specifically, regarding compressor reliability, under constant compressor load and lubrication conditions, a larger crankshaft diameter 31 generally results in better reliability. However, as the crankshaft diameter increases, frictional power consumption also increases, leading to a decrease in compressor efficiency. Therefore, the design of the crankshaft diameter 31 must ensure compressor reliability while minimizing its diameter to maximize efficiency. Based on this, this application sets the outer diameter D1 of the first shaft section 311 to be greater than or equal to 11 mm and less than or equal to 15 mm. This helps ensure the installation accuracy and stability of the stationary scroll plate 32, allowing it to fit tightly onto the first shaft section 311 and maintain a uniform gap with the moving scroll plate 33, reducing the possibility of gas leakage in the compression chamber 301. Setting the outer diameter D2 of the eccentric section 312 to be greater than or equal to 14 mm and less than or equal to 18 mm helps ensure the installation accuracy and stability of the moving scroll plate 33, allowing it to be installed according to a predetermined... The eccentricity rotates stably around the crankshaft 31 axis, ensuring the formation of a stable compression chamber 301 between the moving scroll 33 and the stationary scroll 32. Simultaneously, it ensures that the eccentric section 312 has sufficient strength and rigidity to withstand the radial and tangential forces generated by the moving scroll 33 during operation, effectively improving the reliability of the compressor. Setting the outer diameter D3 of the second shaft section 313 to be greater than or equal to 9mm and less than or equal to 13mm helps ensure proper installation and stable support of the bracket 34, preventing damage to the second shaft section 313 due to excessive local stress, and effectively improving the reliability of the compressor.

[0105] Furthermore, as shown in Figures 4 to 10, in this embodiment, the stationary scroll plate 32 is provided with a first bearing portion 322 on the side away from the moving scroll plate 33, and the first bearing portion 322 has a first bearing hole 323; the moving scroll plate 33 has an eccentric bearing hole 332; and the support 34 is provided with a second bearing portion 341 on the side away from the moving scroll plate 33, and the second bearing portion 341 has a second bearing hole 342.

[0106] Specifically, in this embodiment, the stationary scroll plate 32 has a first bearing portion 322, the bracket 34 has a second bearing portion 341, and the pump body assembly 30 is closer to the bottom of the accommodating cavity 101 than the motor 20. That is, the compressor adopts a bottom-mounted pump body assembly 30 structure. Thus, the presence of the first bearing portion 322 and the second bearing portion 341 can support the crankshaft 31, eliminating the need for an additional bearing on the other side of the motor 20 to support the crankshaft 31. Simultaneously, the first bearing portion 322 and the second bearing portion 341 are closer to the lubricating oil at the bottom of the accommodating cavity 101, ensuring reliable compressor operation without the need for additional bushings. The overall structure is simple and the manufacturing cost is low.

[0107] Specifically, when the outer diameter D1 of the first shaft section 311 (as shown in Figure 11) is less than 11mm, the structural strength of the first shaft section 311 is low. When the compressor is running at high speed, the first shaft section 311 is prone to bending and deformation, and may break in severe cases. When the outer diameter D1 of the first shaft section 311 is greater than 15mm, the weight and manufacturing cost of the crankshaft 31 increase, which is not conducive to the lightweight and miniaturized design of the compressor.

[0108] Specifically, when the outer diameter D2 of the eccentric section 312 (as shown in Figure 11) is less than 14mm, the structural strength of the eccentric section 312 is low, making it difficult for the eccentric section 312 to support the moving scroll plate 33, thus affecting the normal fit between the moving scroll plate 33 and the stationary scroll plate 32; when the outer diameter D2 of the eccentric section 312 is greater than 18mm, the mass of the eccentric section 312 is increased, which leads to an increase in the inertia of the entire crankshaft 31, which has an adverse effect on the use of the compressor.

[0109] Specifically, when the outer diameter D3 of the second shaft section 313 (as shown in Figure 11) is less than 9mm, the structural strength of the second shaft section 313 is low, which means that the second shaft section 313 is insufficient to support the weight of the bracket 34 and other auxiliary components. During the operation of the compressor, the bracket 34 may wobble, thus affecting the stability of the compressor. When the outer diameter D3 of the second shaft section 313 is greater than 13mm, the weight and manufacturing cost of the crankshaft 31 increase, which is not conducive to the lightweight and miniaturized design of the compressor.

[0110] For example, referring to Figure 1, in this embodiment, the motor 20 is sleeved on the first shaft segment 311, the stationary scroll plate 32 is sleeved on the side of the first shaft segment 311 near the eccentric segment 312, the moving scroll plate 33 is sleeved on the eccentric segment 312, and the bracket 34 is sleeved on the side of the second shaft segment 313 near the eccentric segment 312.

[0111] Furthermore, in this embodiment, the outer diameter D1 of the first shaft segment 311 satisfies the relationship: 12.5mm≤D1≤13.5mm. For example, D1 can be set to 12.5mm, 12.6mm, 12.7mm, 12.8mm, 12.9mm, 13mm, 13.1mm, 13.2mm, 13.3mm, 13.4mm, 13.5mm, etc.

[0112] Specifically, when the outer diameter D1 of the first shaft section 311 is less than 12.5mm, the structural strength of the first shaft section 311 is low. When the compressor is running at high speed, the first shaft section 311 is prone to bending and deformation, and may break in severe cases. When the outer diameter D1 of the first shaft section 311 is greater than 13.5mm, the weight and manufacturing cost of the crankshaft 31 increase, which is not conducive to the lightweight and miniaturized design of the compressor.

[0113] Furthermore, in this embodiment, the outer diameter D3 of the second shaft segment 313 satisfies the relationship: 9.5mm≤D3≤11.5mm. For example, D3 can be set to 9.5mm, 9.7mm, 9.9mm, 10mm, 10.2mm, 10.4mm, 10.6mm, 10.8mm, 11mm, 11.2mm, 11.4mm, 11.5mm, etc.

[0114] Specifically, when the outer diameter D3 of the second shaft section 313 is less than 9.5mm, the structural strength of the second shaft section 313 is low, which means that the second shaft section 313 is insufficient to support the weight of the bracket 34 and other auxiliary components. During the operation of the compressor, the bracket 34 may wobble, thereby affecting the stability and reliability of the compressor. When the outer diameter D3 of the second shaft section 313 is greater than 11.5mm, the weight and manufacturing cost of the crankshaft 31 increase, which is not conducive to the lightweight and miniaturized design of the compressor.

[0115] Furthermore, in this embodiment, the outer diameter D4 of the stator 22 (as shown in Figure 1) satisfies the relationship: 96mm≤D4≤104mm. For example, D1 can be set to 96mm, 97mm, 98mm, 99mm, 100mm, 101mm, 102mm, 103mm, 104mm, etc.

[0116] Specifically, to meet the power requirements of the compressor and ensure its reliability, the size of the stator 22 of the motor 20 cannot be too small. While a larger stator 22 generally improves energy efficiency, the improvement diminishes after a certain point, leading to a decrease in cost-effectiveness. Therefore, the size of the motor 20 is subject to certain limitations. The motor's size is determined by the maximum radial dimension and height of the stator 22. Considering that the ratio of the stator 22's maximum radial dimension to its height significantly impacts the compressor's energy efficiency, and that an excessively tall stator 22 would result in an excessively tall rotor 21, causing significant bending deformation of the crankshaft 31 during operation and generating noise, while an excessively short stator 22 would affect the rotor 21's oscillation frequency and the uniformity of electromagnetic force, further contributing to noise issues, the maximum radial dimension and height of the stator 22 are limited, taking into account the motor 20's reliability, cost-effectiveness, and noise levels. To meet the needs of air conditioning systems with cooling capacities ranging from 2500W to 3700W, in this embodiment, the outer diameter D1 of the stator 22 satisfies the relationship: 96mm≤D1≤104mm.

[0117] Furthermore, the outer diameter D5 of the moving scroll disk 33 in this embodiment (as shown in Figure 5) satisfies the relationship: 78mm≤D5≤82mm. For example, D5 can be set to 78mm, 78.5mm, 79mm, 79.5mm, 80mm, 80.5mm, 81mm, 81.5mm, 82mm, etc.

[0118] Specifically, the moving scroll plate 33 is used to house the second scroll tooth 331 and needs to seal and cover the first scroll tooth 321 of the stationary scroll plate 32. The maximum radial dimension of the moving scroll plate 33 is related to the bore diameter of the eccentric bearing hole 332, the tooth thickness of the second scroll tooth 331, the eccentricity of the eccentric section 312, the number of scrolls of the second scroll tooth 331, and the sealing width. Smaller parameters result in smaller maximum radial dimensions of the moving scroll 33. However, excessively small bore diameters in the eccentric bearing hole 332 can lead to excessive surface pressure on the eccentric section 312, causing reliability issues. Insufficient tooth thickness in the second scroll tooth 331 can cause deformation, resulting in meshing friction or even breakage. Insufficient eccentricity can lead to excessive surface pressure on the first and second shaft sections 311 and 313 of the crankshaft 31, causing reliability problems. Insufficient scroll rotations in the second scroll tooth 331 can make it difficult to achieve a large volumetric ratio, leading to undercompression losses and reduced energy efficiency. Insufficient sealing width can cause excessive leakage, reducing compressor efficiency. Therefore, the maximum radial dimension of the moving scroll 33 needs to be limited. Considering the requirements of air conditioning systems with cooling capacities ranging from 2500W to 3700W, in this embodiment, the outer diameter D2 of the moving scroll 33 must be greater than or equal to 78mm; otherwise, the compressor's efficiency and reliability will be significantly affected. The larger the outer diameter of the moving scroll plate 33, the larger the maximum radial dimension of the entire pump body assembly 30, and the more material is used, which reduces the cost-effectiveness of the compressor. Therefore, in this embodiment, the outer diameter D2 of the moving scroll plate 33 must be less than or equal to 82mm.

[0119] Further, referring to Figure 3, the first shaft segment 311 in this embodiment has a first support fitting portion 40 that mates with the first bearing hole 323 or the second bearing hole 342. Along the axial direction of the crankshaft 31, the width W1 of the first support fitting portion 40 (as shown in Figure 3) satisfies the relationship: 22mm ≤ W1 ≤ 35mm. For example, W1 can be set to 22mm, 24mm, 26mm, 28mm, 30mm, 32mm, 34mm, 35mm, etc. It can be understood that the first shaft segment 311 in this embodiment can mate with the first bearing hole 323 to form the first support fitting portion 40, or it can mate with the second bearing hole 342 to form the first support fitting portion 40. Figure 2 of this embodiment shows the case when the first shaft segment 311 mates with the first bearing hole 323.

[0120] Specifically, a larger support width of the first support mating part 40 results in a larger bearing surface, thereby reducing the surface pressure on the first bearing part 322. This reduces the likelihood of wear on the first bearing part 322 or the second bearing part 341, thus lowering the compressor's reliability. However, an excessively large contact area between the first bearing part 322 or the second bearing part 341 and the first shaft section 311 leads to increased frictional energy consumption, which is detrimental to the compressor's energy efficiency. Specifically, when W1 is less than 22mm, the mating length between the first bearing part 322 or the second bearing part 341 and the first shaft section 311 is shortened, reducing the contact area. This results in increased pressure per unit area, exacerbating wear on the first bearing part 322 or the second bearing part 341 and reducing the compressor's operational reliability. When W1 is greater than 35mm, the contact area between the first bearing part 322 or the second bearing part 341 and the first shaft section 311... The excessively large contact area between the first bearing portion 322 or the second bearing portion 341 and the first shaft section 311 increases the frictional force, causing wear on both the first bearing portion 322 or the second bearing portion 341 and the first shaft section 311, reducing the reliability of compressor operation. At the same time, the excessively wide first support fit portion 40 increases the mass of the crankshaft 31, resulting in an increase in the rotational inertia of the crankshaft 31. Consequently, the motor 20 needs to provide a larger starting torque when the compressor starts, increasing the starting load of the motor 20 and raising operating costs.

[0121] Further, referring to Figure 3, the first shaft segment 311 in this embodiment has a first support fitting part 40 that mates with the first bearing hole 323 or the second bearing hole 342. Along the axial direction of the crankshaft 31, the maximum distance L1 between the end of the first support fitting part 40 away from the eccentric segment 312 and the end of the eccentric segment 312 near the first shaft segment 311 (as shown in Figure 3) satisfies the relationship: 30mm≤L1≤45mm. For example, L1 can be set to 30mm, 32mm, 34mm, 36mm, 38mm, 40mm, 42mm, 44mm, 45mm, etc.

[0122] Specifically, since the end of the first shaft section 311 away from the eccentric section 312 is fastened to the rotor 21 of the motor 20 to transmit torque, and the rotor 21 is provided with a balance block with eccentric mass of the balancing scroll 33, when the compressor is running, the balance block on the rotor 21 generates centrifugal force due to rotation. The higher the compressor speed, the greater the centrifugal force, which will act on the first support mating part 40. Since torque = force × lever arm, where force is the centrifugal force generated by the balance block and lever arm is the distance from the end of the first support mating part 40 away from the eccentric section 312 to the eccentric section 312, if the lever arm is too long, the torque acting on the first support mating part 40 will be greater, which will generate a larger load on the first bearing part 322 and reduce the reliability of the first bearing part 322 or the second bearing part 341. Based on this, this embodiment can shorten the length of the lever arm by making L1 satisfy the relationship: 30mm≤L1≤45mm, thereby reducing the torque acting on the first support mating part 40, and further reducing the load on the first bearing part 322 or the second bearing part 341, effectively improving the reliability of the first bearing part 322 or the second bearing part 341.

[0123] According to the torque formula, when L1 is less than 30mm, the force needs to be increased accordingly in order to generate the same torque. In the compressor, if a certain torque is to be maintained to drive the crankshaft 31 to rotate, a smaller lever arm means that the motor 20 needs to output a larger force, which will cause the motor 20 to be overloaded and shorten its service life. When L1 is greater than 45mm, the torque is too large, which will cause the crankshaft 31 to bend and deform during rotation, reducing the reliability of the compressor.

[0124] Further, referring to Figures 1 to 3 and Figure 12, the crankshaft 31 in this embodiment is provided with an oil supply channel 314, which extends from the end of the second shaft segment 313 toward the direction close to the first shaft segment 311; the outer surface of the first support fitting part 40 is provided with a first oil groove 41, which communicates with the oil supply channel 314 through a first oil hole 42; the first shaft segment 311 is provided with an annular groove 325, which is located between the first support fitting part 40 and the eccentric segment 312 and is arranged around the circumference of the first shaft segment 311; the first oil groove 41 extends along the axial direction of the crankshaft 31 and extends from the first support fitting part 40 to the annular groove 325.

[0125] Specifically, the first oil groove 41 is provided to guide the lubricating oil to the first support mating part 40, thereby improving the friction state of this part, reducing bearing friction power consumption, effectively improving the energy efficiency of the compressor, and enhancing the reliability of the bearing in this part. Meanwhile, in this embodiment, since the first oil groove 41 extends from the first support mating part 40 to the annular groove 325, that is, at least a portion of the first oil groove 41 away from the eccentric section 312 is disposed on the first support mating part 40, while at least a portion of the first oil groove 41 near the eccentric section 312 passes through the first support mating part 40 and is disposed on the annular groove 325, the lubricating oil can flow from one side of the first support mating part 40 to the other through only one path, thus ensuring that the lubricating oil can fully lubricate the entire first support mating part 40.

[0126] Further, referring to Figure 16, in the projection along the direction from the first shaft segment 311 to the eccentric segment 312, the projections of both the first shaft segment 311 and the eccentric segment 312 include circles. Taking the center of the circle of the first shaft segment 311 as the endpoint, and passing through the center of the circle of the eccentric segment 312, a first ray 50 is drawn. With the first ray 50 as 0° and counterclockwise as the direction of rotation of the crankshaft 31 and the direction of increasing angle, the first oil groove 41 is disposed on the outer surface of the first shaft segment 311 and is located between 0° and 180° and between 270° and 360°.

[0127] Specifically, in this embodiment, the first ray 50 is taken as the 0-degree angle of the y-axis, and counterclockwise is taken as the direction of rotation and angle increase of the crankshaft 31. This ensures that the first oil groove 41 can only be located between 0° and 180° and between 270° and 360°, meaning the first oil groove 41 cannot be set within the 180° to 270° angle range. This is because the oil groove's position needs to avoid the load-bearing parts of the crankshaft 31; otherwise, it will affect the lubrication of the bearings by the lubricating oil. If the oil groove is located at the load-bearing part, it will reduce the bearing's bearing area, resulting in excessive surface pressure and easy deformation of the crankshaft 31. In other words, in this embodiment, the range of 180° to 270° is the bearing part of the first shaft segment 311. Therefore, the location of the first oil groove 41 needs to avoid this bearing part so as not to affect the lubrication of the first bearing part 322. At the same time, since the first oil groove 41 is not arranged on the bearing part, the bearing area of ​​the first bearing part 322 or the second bearing part 341 will not be reduced, thereby preventing the first bearing part 322 or the second bearing part 341 and the first shaft segment 311 from deforming during the operation of the compressor.

[0128] Further, referring to Figure 12, the first support mating part 40 in this embodiment includes two support sections 43 arranged sequentially along the crankshaft 31 axial direction. The outer surfaces of the two support sections 43 each have a first oil groove 41. In the two support sections 43, the width of the support section 43 arranged closer to the eccentric section 312 along the crankshaft 31 axial direction is greater than the width of the support section 43 arranged further away from the eccentric section 312 along the crankshaft 31 axial direction.

[0129] Specifically, the arrangement of the two support sections 43 ensures that the width W1 of the first support mating part 40 is greater than or equal to 22mm and less than or equal to 35mm, thereby reducing the surface pressure on the first bearing part 322 and thus reducing the possibility that the first bearing part 322 is prone to wear and thus reduces the reliability of the compressor. At the same time, in this embodiment, the side of the first bearing part 322 near the eccentric section 312 of the crankshaft 31 bears the main load from the eccentric section 312. In order to ensure that the first bearing part 322 can stably support the crankshaft 31 and reduce the wear and deformation of the first bearing part 322, a larger support mating width is required. On the other side of the first bearing part 322 away from the eccentric section 312, the load is relatively small, so a larger support mating width is not required as for the bearing on the side near the eccentric section 312. In other words, by making the width of the support section 43 located near the eccentric section 312 along the crankshaft 31 axial direction greater than the width of the support section 43 located away from the eccentric section 312 along the crankshaft 31 axial direction, this embodiment can ensure that the end of the first bearing portion 322 near the eccentric section 312 can bear a larger load, thereby stably supporting the crankshaft 31 and reducing the wear and deformation of the first bearing portion 322.

[0130] Further, referring to Figure 12, the outer surface of the first support mating part 40 in this embodiment is provided with a first annular groove 45. The first annular groove 45 is arranged around the first shaft segment 311 in the circumferential direction, and the first annular groove 45 is located between the two support segments 43 to at least store lubricating oil.

[0131] Specifically, in this embodiment, the lubricating oil at the bottom of the accommodating cavity 101 enters the crankshaft 31 through the oil supply channel 314, and then flows into the first oil groove 41 through the first oil hole 42. Since the first oil groove 41 is provided on the outer surface of the first support mating part 40, when the compressor is running, some of the lubricating oil in the first oil groove 41 will accumulate in the first annular groove 45, which is beneficial to lubricate the friction parts between the first bearing part 322 and the first shaft section 311. At the same time, the lubricating oil accumulated in the first annular groove 45 is more conducive to improving the reliability of the compressor when it starts up. The reason is that when the compressor starts up, it takes a certain amount of time for the lubricating oil in the oil storage space 102 to reach the bearing lubrication part, and it cannot lubricate the bearing in time. However, the lubricating oil accumulated in the first annular groove 45 can lubricate the first bearing part 322, effectively ensuring the reliability of the compressor during operation and effectively improving the compressor's energy efficiency.

[0132] Further, referring to Figure 3, the eccentric segment 312 in this embodiment has a second support fitting part 60 that mates with the eccentric bearing hole 332. Along the axial direction of the crankshaft 31, the width W2 of the second support fitting part 60 (as shown in Figure 3) satisfies the relationship: 12mm≤W2≤18mm. For example, W2 can be set to 12mm, 12.5mm, 13mm, 13.5mm, 14mm, 14.5mm, 15mm, 15.5mm, 16mm, 16.5mm, 17mm, 17.5mm, 18mm, etc.

[0133] Specifically, the larger the support width of the second support mating part 60, the larger the bearing surface will be, thereby reducing the surface pressure on the eccentric bearing hole 332, and thus reducing the possibility that the eccentric bearing hole 332 is easily worn and the compressor reliability is reduced. However, if the contact area between the moving scroll plate 33 and the eccentric section 312 is too large, it will lead to increased frictional power consumption, which is not conducive to the energy efficiency of the compressor. Specifically, when W2 is less than 12mm, the fitting length between the eccentric bearing hole 332 and the eccentric section 312 of the moving scroll 33 is shortened, reducing the contact area between the moving scroll 33 and the eccentric section 312. This results in an increase in the pressure per unit area, which in turn exacerbates the wear on the moving scroll 33 and reduces the reliability of the compressor operation. When W2 is greater than 18mm, the contact area between the eccentric bearing hole 332 and the eccentric section 312 of the moving scroll 33 is too large, which increases the friction between the eccentric bearing hole 332 and the eccentric section 312. This causes both the eccentric bearing hole 332 and the eccentric section 312 to wear, reducing the reliability of the compressor operation.

[0134] Further, referring to Figure 3, the eccentric segment 312 in this embodiment has a second support fitting portion 60 that mates with the eccentric bearing hole 332. The center of the width of the second support fitting portion 60 along the crankshaft 31 axial direction is located between the end face of the moving scroll disk 33 facing away from the second scroll tooth portion 331 at half the height of the second scroll tooth portion 331 along the crankshaft 31 axial direction. It should be noted that in this embodiment, the "center of the width of the second support fitting portion 60 along the crankshaft 31 axial direction" refers to the center point or center plane located at the center position of the width of the first support fitting portion 40 along the crankshaft 31 axial direction within the projection along the radial direction of the crankshaft 31. It should also be noted that in this embodiment, the "center of the width of the second support fitting portion 60 along the crankshaft 31 axial direction" refers to the position shown by plane F in Figure 3, and "half the height of the second scroll tooth portion 331 along the crankshaft 31 axial direction" refers to the position shown by plane E in Figure 3.

[0135] Specifically, in this embodiment, the moving scroll disk 33 is a solid structure, which means that it has high strength and rigidity, and can withstand greater pressure without easily deforming. The second scroll tooth 331 is a cantilever structure with relatively thin walls. The characteristic of the cantilever structure is that one end is fixed and the other end is suspended. That is, the side of the second scroll tooth 331 closer to the moving scroll disk 33 is fixed to the moving scroll disk 33, and the side of the second scroll tooth 331 away from the moving scroll disk 33 is suspended. The load-bearing capacity of this structure is relatively weak.

[0136] Based on this, when the eccentric section 312 is fitted with the eccentric bearing hole 332, since the moving scroll 33 has a strong load-bearing capacity and the second scroll tooth 331 has a weak load-bearing capacity, in order to ensure the reliability of the bearing, the center of the width of the second support fitting part 60 along the axial direction of the crankshaft 31 should be reasonably arranged. If the center is too close to the second scroll tooth 331, the second scroll tooth 331 may easily deform during the rotation of the crankshaft 31, thus affecting the normal operation of the bearing. Therefore, in this embodiment, by setting the center of the width of the second support mating part 60 along the axial direction of the crankshaft 31 at half the height of the second scroll tooth part 331 along the axial direction of the crankshaft 31 and between the end face of the moving scroll disk 33 facing away from the second scroll tooth part 331, the strong load-bearing capacity of the moving scroll disk 33 can be fully utilized, so that most of the load can be transmitted to the moving scroll disk 33 through the eccentric bearing hole 332, reducing the unreasonable excessive load borne by the second scroll tooth part 331, thereby ensuring a stable and reliable support environment for the bearing during operation and effectively improving the reliability of the crankshaft 31 during rotation.

[0137] Further, referring to Figure 3, the second shaft segment 313 in this embodiment has a third support fitting portion 70 that mates with the first bearing hole 323 or the second bearing hole 342. Along the axial direction of the crankshaft 31, the width W3 of the third support fitting portion 70 (as shown in Figure 3) satisfies the relationship: 10mm ≤ W3 ≤ 18mm. For example, W3 can be set to 10mm, 11mm, 12mm, 13mm, 14mm, 15mm, 16mm, 17mm, 18mm, etc. It is understood that the second shaft segment 313 in this embodiment can mate with the first bearing hole 323 to form the third support fitting portion 70, or it can mate with the second bearing hole 342 to form the third support fitting portion 70. Figure 2 of this embodiment shows the case where the second shaft segment 313 mates with the second bearing hole 342.

[0138] Specifically, the larger the support width of the third support mating part 70, the larger the bearing surface will be, thereby reducing the surface pressure on the first bearing part 322 or the second bearing part 341, and thus reducing the possibility that the first bearing part 322 or the second bearing part 341 is easily worn and the compressor reliability is reduced. However, if the contact area between the first bearing part 322 or the second bearing part 341 and the second shaft section 313 is too large, it will lead to increased frictional power consumption, which is detrimental to the energy efficiency of the compressor. When W3 is less than 10mm, the fitting length between the first bearing part 322 or the second bearing part 341 and the second shaft section 313 is shortened, reducing the contact area between the first bearing part 322 or the second bearing part 341 and the second shaft section 313. This results in an increase in the pressure per unit area, which in turn exacerbates the wear on the first bearing part 322 of the stationary scroll plate 32 or the second bearing part 341 of the bracket 34, reducing the reliability of the compressor operation. When W3 is greater than 18mm, the contact area between the first bearing part 322 or the second bearing part 341 and the second shaft section 313 is too large, which increases the friction between the first bearing part 322 or the second bearing part 341 and the second shaft section 313. This causes wear on both the first bearing part 322 or the second bearing part 341 and the second shaft section 313, reducing the reliability of the compressor operation.

[0139] Further, referring to Figure 12, in this embodiment, the first shaft segment 311 has a first support fitting part 40 that mates with the first bearing hole 323 or the second bearing hole 342, and the outer surface of the first support fitting part 40 is provided with a first oil groove 41; the eccentric segment 312 has a second support fitting part 60 that mates with the eccentric bearing hole 332, and the second support fitting part 60 has a second oil groove 61. The second oil groove 61 is disposed along the axial direction of the crankshaft 31 on the outer surface of the second support fitting part 60, and the second oil groove 61 is connected to the first oil groove 41 through an annular groove 325.

[0140] Specifically, the second oil groove 61 is provided to lubricate the mating surface between the eccentric section 312 and the eccentric bearing hole 332, thereby reducing friction between the eccentric bearing hole 332 and the eccentric section 312. In this embodiment, the lubricating oil at the bottom of the accommodating cavity 101 enters the crankshaft 31 through the oil supply channel 314, and then flows into the first oil groove 41 through the first oil hole 42. Since the second oil groove 61 is connected to the first oil groove 41 through the annular groove 325, the lubricating oil in the first oil groove 41 flows into the second oil groove 61, thereby lubricating the mating surface between the eccentric section 312 and the eccentric bearing hole 332. That is to say, the second oil groove 61 in this embodiment is connected to the first oil groove 41, which is conducive to the flow of lubricating oil, thereby better lubricating the mating surface between the eccentric bearing hole 332 and the eccentric section 312.

[0141] Further, referring to Figure 12, the crankshaft 31 in this embodiment is provided with an oil supply channel 314, which extends from the end of the second shaft segment 313 toward the direction close to the first shaft segment 311; the eccentric segment 312 has a second support fitting part 60 that mates with the eccentric bearing hole 332, the second support fitting part 60 has a third oil groove 62, the third oil groove 62 is located on the outer surface of the second support fitting part 60 and extends along the axial direction of the crankshaft 31, and the width of the third oil groove 62 along the axial direction of the crankshaft 31 is smaller than the width of the second support fitting part 60 along the axial direction of the crankshaft 31, and the third oil groove 62 communicates with the oil supply channel 314 through the second oil hole 63.

[0142] Specifically, in this embodiment, the outer surface of the eccentric segment 312 is provided with both a second oil groove 61 and a third oil groove 62. As described above, the lubricating oil in the second oil groove 61 originates from the first oil groove 41. When the compressor starts, the lubricating oil first reaches the first oil groove 41 from the oil supply channel 314, and then flows into the second oil groove 61. This results in the lubricating oil not reaching the area between the eccentric segment 312 and the eccentric bearing hole 332 in a timely manner, making it difficult to lubricate the mating surfaces between them. Therefore, in this embodiment, a third oil groove 62 communicating with the oil supply channel 314 is provided on the outer surface of the second support mating part 60. Thus, when the compressor starts, the lubricating oil in the oil supply channel 314 can flow through the second oil hole 63 into the third oil groove 62, thereby timely lubricating the mating surfaces between the eccentric bearing hole 332 and the eccentric segment 312, effectively ensuring the reliability and stability of the eccentric bearing hole 332 and the eccentric segment 312.

[0143] Further, referring to Figure 13, the second oil groove 61 in this embodiment has a first groove edge 611 and a second groove edge 612 arranged opposite to each other along the circumference of the crankshaft 31. The angle between the line connecting the first groove edge 611 and the center of the eccentric segment 312 and the line connecting the second groove edge 612 and the center of the eccentric segment 312 is θ1. The third oil groove 62 has a third groove edge 621 and a fourth groove edge 622 arranged opposite to each other along the circumference of the crankshaft 31. The angle between the line connecting the third groove edge 621 and the center of the eccentric segment 312 and the line connecting the fourth groove edge 622 and the center of the eccentric segment 312 is θ2. Among them, θ1 and θ2 satisfy the relationship that θ1+θ2≥30°, such as 30°, 32°, 34°, 35°, 36°, 38°, 40°, etc. This configuration reduces the contact area between the eccentric section 312 and the eccentric bearing hole 332, thereby reducing frictional power consumption. At the same time, it improves the flow of lubricating oil on the outer surface of the eccentric section 312, thereby improving the lubrication of the mating surfaces between the eccentric bearing hole 332 and the eccentric section 312, effectively improving the energy efficiency of the compressor, and effectively ensuring the reliability of the compressor.

[0144] Further, referring to Figure 17, in the projection along the direction from the first shaft segment 311 to the eccentric segment 312, the projections of both the first shaft segment 311 and the eccentric segment 312 include circles. Taking the center of the circle of the first shaft segment 311 as the endpoint and passing through the center of the circle of the eccentric segment 312, a first ray 50 is drawn. With the first ray 50 as 0° and counterclockwise as the direction of rotation of the crankshaft 31 and the direction of increasing angle, the second oil groove 61 and the third oil groove 62 are disposed on the outer surface of the eccentric segment 312 and are located between 90° and 360°.

[0145] Specifically, in this embodiment, the first ray 50 is taken as the 0-degree angle of the y-axis, and counterclockwise is taken as the direction of rotation and angle increase of the crankshaft 31. This ensures that the second oil groove 61 and the third oil groove 62 can only be located between 90° and 360°, meaning they cannot be positioned within the 0° to 90° angle range. This is because the oil groove positions need to avoid the load-bearing parts of the crankshaft 31; otherwise, it will affect the lubrication of the bearings. If the oil grooves are located at the load-bearing parts, the bearing area will be reduced, resulting in excessive surface pressure and easy deformation of the crankshaft 31. In other words, in this embodiment, the 0-90 degree angle range is the bearing part of the eccentric section 312. Therefore, the positions of the second oil groove 61 and the third oil groove 62 need to avoid this bearing part, so as not to affect the lubricating oil to lubricate the mating surface between the eccentric bearing hole 332 and the eccentric section 312. At the same time, since the second oil groove 61 and the third oil groove 62 are not arranged on the bearing part, the bearing area of ​​the eccentric bearing hole 332 will not be reduced, thereby avoiding deformation of the eccentric section 312 and the eccentric bearing hole 332 during the operation of the compressor.

[0146] Further, referring to Figure 14, the crankshaft 31 in this embodiment is provided with an oil supply channel 314, which extends from the end of the second shaft segment 313 toward the direction close to the first shaft segment 311; the second shaft segment 313 has a third support fitting part 70 that mates with the first bearing hole 323 or the second bearing hole 342, and the outer surface of the third support fitting part 70 is provided with a fourth oil groove 71, which communicates with the oil supply channel 314 through a third oil hole 72, and the width of the fourth oil groove 71 along the axial direction of the crankshaft 31 is smaller than the width of the third support fitting part 70 along the axial direction of the crankshaft 31.

[0147] Specifically, the fourth oil groove 71 is provided to guide lubricating oil to the third support mating part 70, thereby improving the friction state of this part, reducing bearing friction power consumption, effectively improving the energy efficiency of the compressor, and enhancing the reliability of the bearing in this part. In this embodiment, the lubricating oil at the bottom of the accommodating cavity 101 enters the crankshaft 31 through the oil supply channel 314, and then flows into the fourth oil groove 71 through the third oil hole 72, thereby lubricating the mating surfaces between the first bearing part 322 or the second bearing part 341 and the second shaft section 313, effectively improving the reliability and stability of the compressor.

[0148] Further, referring to Figure 18, in the projection along the direction from the first shaft segment 311 to the eccentric segment 312, the projections of both the first shaft segment 311 and the eccentric segment 312 include circles. Taking the center of the circle of the first shaft segment 311 as the endpoint and passing through the center of the circle of the eccentric segment 312, a first ray 50 is drawn. With the first ray 50 as 0° and counterclockwise as the direction of rotation of the crankshaft 31 and the direction of increasing angle, the fourth oil groove 71 is disposed on the outer surface of the second shaft segment 313 and is located between 0° and 210° and between 270° and 360°.

[0149] Specifically, in this embodiment, the first ray 50 is taken as the 0-degree angle of the y-axis, and counterclockwise is taken as the direction of rotation and angle increase of the crankshaft 31. This ensures that the fourth oil groove 71 can only be located between 0° and 210° and between 270° and 360°, meaning the fourth oil groove 71 cannot be set within the 210° to 270° angle range. This is because the oil groove's location needs to avoid the load-bearing parts of the crankshaft 31; otherwise, it will affect the lubrication of the bearings by the lubricating oil. If the oil groove is located at the load-bearing part, it will reduce the bearing's bearing area, resulting in excessive surface pressure and making the crankshaft 31 prone to deformation. In other words, in this embodiment, the 210-270 degree angle range is the bearing part of the second shaft section 313. Therefore, the fourth oil groove 71 needs to be set to avoid this bearing part so as not to affect the lubricating oil to lubricate the mating surface between the second bearing part 341 and the second shaft section 313. At the same time, since the fourth oil groove 71 is not arranged on the bearing part, it will not reduce the bearing area of ​​the second bearing part 341, thereby avoiding deformation of the second bearing part 341 and the second shaft section 313 during the operation of the compressor.

[0150] Further, referring to Figures 19 and 20, in this embodiment, the first shaft segment 311 has a first support fitting portion 40 that mates with the first bearing hole 323 or the second bearing hole 342, and the outer surface of the first support fitting portion 40 is provided with a first oil groove 41; the eccentric segment 312 has a second support fitting portion 60 that mates with the eccentric bearing hole 332, and the outer surface of the second support fitting portion 60 is provided with a second oil groove 61 and a third oil groove 62; the second shaft segment 313 has a third support fitting portion 60 that mates with the first bearing hole 323 or the second bearing hole 342. The outer surface of the bearing mating part 70 and the third support mating part 70 is provided with a fourth oil groove 71; wherein, the first oil groove 41, the second oil groove 61, the third oil groove 62 and the fourth oil groove 71 all include a straight oil groove 100 or a spiral oil groove 110, and the cross-sectional area of ​​the first oil groove 41, the second oil groove 61, the third oil groove 62 and the fourth oil groove 71 (the area of ​​the cross section obtained by cutting the first oil groove 41, the second oil groove 61, the third oil groove 62 or the fourth oil groove 71 along the direction perpendicular to the axis of the crankshaft 31) is greater than or equal to 0.35 mm. 2 For example, 0.35mm 2 0.36mm 2 0.38mm 2 0.40mm 2 0.42mm 2 0.44mm 2 wait.

[0151] Specifically, in this embodiment, the first oil tank 41, the second oil tank 61, the third oil tank 62, and the fourth oil tank 71 can be provided as straight oil tanks (as shown in Figure 19) or as spiral oil tanks 110 (as shown in Figure 20), but the cross-sectional area of ​​all four must be greater than or equal to 0.35 mm. 2 This configuration effectively ensures the fluidity of the lubricating oil within each oil groove. It is understood that the straight oil groove 100 has a simple structure, is easy to manufacture, and has low manufacturing costs; the spiral oil groove 110 has guiding properties, which facilitates the smooth flow of lubricating oil, thereby better lubricating and removing heat from the friction pairs, effectively improving the reliability of the compressor. For example, Figure 19 of this embodiment shows the case where the first oil groove 41 is configured as a straight oil groove 100; Figure 20 shows the case where the first oil groove 41 is configured as a spiral oil groove 110.

[0152] However, when the cross-sectional areas of the first oil tank 41, the second oil tank 61, the third oil tank 62, and the fourth oil tank 71 are all less than 0.35 mm... 2 When this happens, the amount of lubricating oil in the oil sump decreases, making it impossible to form a sufficiently thick oil film between the crankshaft 31 and the bearings and other mating parts. This leads to increased friction, which in turn causes accelerated wear between the crankshaft 31 and the bearings, shortening the compressor's service life and reducing its reliability.

[0153] Furthermore, in this embodiment, the first shaft segment 311 has a first fitting clearance with the first bearing hole 323 or the second bearing hole 342. Along the radial direction of the crankshaft 31, the width A1 of the first fitting clearance satisfies the relationship: 0.015mm≤A1≤0.04mm. For example, A1 can be set to 0.015mm, 0.016mm, 0.018mm, 0.02mm, 0.022mm, 0.024mm, 0.026mm, 0.028mm, 0.03mm, 0.032mm, 0.034mm, 0.036mm, 0.038mm, 0.04mm, etc.

[0154] Specifically, the existence of the first fitting clearance facilitates the formation of a load-bearing oil film between the first shaft section 311 and the first bearing hole 323 or the second bearing hole 342, thereby improving the reliability of the friction pair of the first bearing portion 322 or the second bearing portion 341 and reducing the frictional power consumption of the first bearing portion 322 or the second bearing portion 341, effectively improving the reliability and energy efficiency of the compressor. When A1 is less than 0.015mm, the lubricating oil has difficulty flowing smoothly within the first fitting clearance, making it difficult to form an oil film between the first shaft section 311 and the first bearing hole 323 or the second bearing hole 342. This increases the friction between the first shaft section 311 and the first bearing portion 322 or the second bearing portion 341, leading to accelerated wear of the stationary scroll plate 32 or the bracket 34 and the crankshaft 31, shortening the compressor's service life. When A1 is greater than 0.04mm, the larger clearance causes the crankshaft 31 to wobble significantly during rotation, thereby compromising the rotational stability of the crankshaft 31 and reducing the compressor's reliability.

[0155] Furthermore, in this embodiment, there is a second fitting clearance between the eccentric section 312 and the eccentric bearing hole 332. Along the radial direction of the crankshaft 31, the width A2 of the second fitting clearance satisfies the relationship: 0.015mm≤A2≤0.04mm. For example, A2 can be set to 0.015mm, 0.016mm, 0.018mm, 0.02mm, 0.022mm, 0.024mm, 0.026mm, 0.028mm, 0.03mm, 0.032mm, 0.034mm, 0.036mm, 0.038mm, 0.04mm, etc.

[0156] Specifically, the existence of the second fitting clearance facilitates the formation of a load-bearing oil film between the eccentric section 312 and the eccentric bearing bore 332, thereby improving the reliability of the friction pair of the eccentric bearing bore 332 and reducing the frictional power consumption of the eccentric bearing bore 332, effectively improving the reliability and energy efficiency of the compressor. However, when A2 is less than 0.015mm, the lubricating oil has difficulty flowing smoothly within the second fitting clearance, making it difficult to form an oil film between the eccentric section 312 and the eccentric bearing bore 332. This increases the friction between the eccentric section 312 and the eccentric bearing bore 332, leading to accelerated wear of the moving scroll 33 and the crankshaft 31, and shortening the compressor's service life. When A2 is greater than 0.04mm, the larger clearance causes the crankshaft 31 to wobble significantly during rotation, thus compromising the rotational stability of the crankshaft 31 and reducing the reliability of the compressor.

[0157] Furthermore, in this embodiment, the second shaft segment 313 has a third fitting clearance with the first bearing hole 323 or the second bearing hole 342. Along the radial direction of the crankshaft 31, the width A3 of the third fitting clearance satisfies the relationship: 0.015mm≤A3≤0.04mm. For example, A3 can be set to 0.015mm, 0.016mm, 0.018mm, 0.02mm, 0.022mm, 0.024mm, 0.026mm, 0.028mm, 0.03mm, 0.032mm, 0.034mm, 0.036mm, 0.038mm, 0.04mm, etc.

[0158] Specifically, the existence of the third fitting clearance facilitates the formation of a load-bearing oil film between the second shaft section 313 and the first bearing hole 323 or the second bearing hole 342, thereby improving the reliability of the friction pair of the first bearing part 322 or the second bearing part 341 and reducing the frictional power consumption of the first bearing part 322 or the second bearing part 341, effectively improving the reliability and energy efficiency of the compressor. However, when A3 is less than 0.015mm, the lubricating oil has difficulty flowing smoothly within the third fitting clearance, making it difficult to form an oil film between the second shaft section 313 and the first bearing hole 323 or the second bearing hole 342. This increases the friction between the second shaft section 313 and the first bearing part 322 or the second bearing part 341, leading to accelerated wear of the stationary scroll plate 32 or the bracket 34 and the crankshaft 31, shortening the compressor's service life. When A3 is greater than 0.04mm, the larger clearance causes significant shaking of the crankshaft 31 during rotation, thereby compromising the rotational stability of the crankshaft 31 and reducing the reliability of the compressor.

[0159] Further, referring to Figures 23 and 24, in this embodiment, the first shaft segment 311 has a first support fitting portion 40 that mates with the first bearing hole 323 or the second bearing hole 342. The outer diameter of the first support fitting portion 40 gradually decreases in the direction away from the eccentric segment 312. That is to say, in this embodiment, the outer diameter of the first support fitting portion 40 has a gradient structure, and this outer diameter gradually decreases in the direction away from the eccentric segment 312.

[0160] Specifically, in this embodiment, the stationary scroll plate 32 has a first bearing portion 322 and a first bearing hole 323. The first bearing portion 322, through the first bearing hole 323, sleeves the stationary scroll plate 32 onto the side of the first shaft segment 311 near the eccentric segment 312. After the stationary scroll plate 32 is installed, the side of the first bearing portion 322 near the eccentric segment 312 will be subjected to load, causing the first shaft segment 311 to tilt in the first bearing hole 323, thereby causing the first shaft segment 311 to tilt. Stress concentration easily occurs at the load-bearing portion away from the eccentric segment 312, leading to wear on the first shaft segment 311 and the first bearing portion 322. Similarly, since the bracket 34 in this embodiment has a second bearing portion 341 with a second bearing hole 342, after the second bearing portion 341 sleeves the bracket 34 on the side of the first shaft segment 311 near the eccentric segment 312 through the second bearing hole 342, stress concentration also occurs at the load-bearing portion of the first shaft segment 311 away from the eccentric segment 312. Therefore, in this embodiment, the outer diameter of the first support fitting portion 40 gradually decreases along the direction away from the eccentric segment 312, that is, the first support fitting portion 40 has a tapered outer diameter structure. In this way, when the first shaft segment 311 is under load, the outer surface of the first shaft segment 311 can fit in close contact with the inside of the first bearing hole 323 or the second bearing hole 342, thereby improving stress concentration and effectively improving the reliability and stability of the bearing.

[0161] Further, referring to Figure 24, the taper C of the first support fitting part 40 in this embodiment satisfies the relationship: C = H1 / L2, and 1 / 2000 ≤ C ≤ 1 / 1000. For example, C can be set to 1 / 2000, 1 / 1800, 1 / 1600, 1 / 1400, 1 / 1200, 1 / 1000, etc., where H1 is the maximum distance between the first support fitting part 40 and the inner wall of the first bearing hole 323 or the second bearing hole 342, and L2 is the height of the first support fitting part 40 along the crankshaft 31 axial direction.

[0162] Specifically, when C is less than 1 / 2000, it is difficult to achieve the effect of the outer surface of the first shaft section 311 fitting with the inside of the first bearing hole 323 or the second bearing hole 342, thus making it difficult to improve stress concentration and reducing the reliability and stability of the bearing; when C is greater than 1 / 1000, it is difficult to form an oil film between the first shaft section 311 and the first bearing part 322 or the second bearing part 341, thus increasing the friction between the first shaft section 311 and the first bearing part 322 or the second bearing part 341, resulting in accelerated wear of the stationary scroll plate 32 or the bracket 34 and the crankshaft 31, and shortening the service life of the compressor.

[0163] Furthermore, referring to Figure 23, in this embodiment, a third oil hole 72 is provided between the eccentric bearing hole 332 of the moving scroll disk 33 and the crankshaft 31.

[0164] Specifically, since the eccentric bearing hole 332 on the moving scroll 33 in this embodiment is subjected to a large load and complex gas load, and has an overturning moment, it is prone to deformation during compressor operation. In this embodiment, the third oil hole 72 is set between the moving scroll 33 and the crankshaft 31. In this way, it can provide additional support for the eccentric bearing hole 332 of the moving scroll 33, enhance the rigidity of the bearing, especially when subjected to complex gas load and overturning moment, the third oil hole 72 can effectively distribute the load and reduce the deformation of the bearing, thereby ensuring the normal operation of the moving scroll 33 and effectively improving the reliability and stability of the bearing.

[0165] Optionally, the third oil hole 72 in this embodiment is made of at least one of polytetrafluoroethylene (PTFE), carbon material, and aluminum alloy. That is to say, in this embodiment, the third oil hole 72 can be made of PTFE, carbon material, or aluminum alloy alone, or it can be made of at least two of PTFE, carbon material, and aluminum alloy, and they can be mixed in any proportion. This application does not make any specific limitation.

[0166] Specifically, polytetrafluoroethylene, carbon materials, and aluminum alloy materials have advantages such as good lubricity and high structural strength, which can help reduce the friction between the eccentric bearing hole 332 and the eccentric section 312, reduce the wear between the moving scroll disk 33 and the crankshaft 31, and effectively improve the reliability and stability of the bearing.

[0167] Further, referring to Figure 25, in this embodiment, a second annular groove 324 is provided on the side of the stationary vortex disk 32 or the support 34 near the eccentric section 312. The second annular groove 324 is arranged around the outer periphery of the first bearing hole 323 along the circumference of the stationary vortex disk 32 or around the outer periphery of the second bearing hole 342 along the circumference of the support 34, and is spaced apart from the first bearing hole 323 or the second bearing hole 342. Figure 25 of this embodiment shows the case where the second annular groove 324 is provided on the side of the stationary vortex disk 32 near the eccentric section 312.

[0168] Specifically, in this embodiment, the stationary scroll plate 32 has a first bearing portion 322 and a first bearing hole 323. The first bearing portion 322, through the first bearing hole 323, sleeves the stationary scroll plate 32 onto the side of the first shaft segment 311 near the eccentric segment 312. After the stationary scroll plate 32 is installed, the side of the first shaft segment 311 near the eccentric segment 312 will be subjected to load, causing the first shaft segment 311 to tilt in the first bearing hole 323, thereby causing the first shaft segment 311 to tilt. Stress concentration easily occurs in the load-bearing parts far from the eccentric section 312, leading to wear on the first shaft section 311 and the first bearing portion 322. Similarly, since the bracket 34 in this embodiment has a second bearing portion 341 with a second bearing hole 342, stress concentration also occurs in the load-bearing parts of the first shaft section 311 far from the eccentric section 312 after the second bearing portion 341 fits the bracket 34 onto the side of the first shaft section 311 near the eccentric section 312 through the second bearing hole 342. Therefore, this embodiment provides a second annular groove 324 on the side of the stationary scroll 32 or the bracket 34 near the eccentric section 312. In this way, when the first bearing portion 322 or the second bearing portion 341 is under load, the inside of the first bearing hole 323 or the second bearing hole 342 can fit against the outer surface of the first shaft section 311, thereby improving stress concentration and effectively improving the reliability and stability of the bearing. In addition, the second annular groove 324 can also be used to store lubricating oil to lubricate the mating area between the stationary vortex disk 32 or the bracket 34 and the first shaft segment 311.

[0169] Furthermore, along the radial direction of the crankshaft 31, the minimum thickness T1 between the side of the second annular groove 324 near the first bearing hole 323 and the first bearing hole 323, or between the side of the second annular groove 324 near the second bearing hole 342 and the second bearing hole 342 (as shown in Figure 25) satisfies the relationship: T1≥1.5mm. For example, T1 can be set to 1.5mm, 1.6mm, 1.8mm, 2mm, etc.

[0170] Specifically, when the second annular groove 324 is provided on the stationary volute 32, and T1 is less than 1.5 mm, the thickness between the second annular groove 324 and the first bearing hole 323 on the side of the second annular groove 324 closest to the first bearing hole 323 is too small. This results in a weaker structure on the side of the stationary volute 32 near the first bearing hole 323, making the stationary volute 32 prone to deformation and reducing the reliability and stability of the first bearing part 322. Similarly, when the second annular groove 324 is provided on the bracket 34, and T1 is less than 1.5 mm, the thickness between the second annular groove 324 and the second bearing hole 342 on the side of the second annular groove 324 closest to the second bearing hole 342 is too small. This results in a weaker structure on the side of the bracket 34 near the second bearing hole 342, making the bracket 34 prone to deformation and reducing the reliability and stability of the second bearing part 341.

[0171] Furthermore, along the radial direction of the crankshaft 31, the width D6 of the second annular groove 324 (as shown in Figure 25) satisfies the relationship: 1.5mm≤D6≤2.5mm. For example, D6 can be set to 1.5mm, 1.6mm, 1.8mm, 1.9mm, 2mm, 2.2mm, 2.4mm, 2.5mm, etc.

[0172] Specifically, when D6 is less than 1.5mm, the width of the second annular groove 324 is too small, which reduces the amount of lubricating oil stored. During long-term operation of the compressor, it is difficult to maintain a sufficiently thick sealing oil film, which causes gas in the compression chamber 301 to leak from the tiny gap, reducing the compressor's compression efficiency and reliability. When D6 is greater than 2.5mm, the wider second annular groove 324 will weaken the radial strength of the stationary scroll plate 32 or the support 34, which will make the stationary scroll plate 32 or the support 34 prone to deformation during compressor operation.

[0173] Furthermore, along the axial direction of the crankshaft 31, the height H2 of the second annular groove 324 (as shown in Figure 25) satisfies the relationship: 4mm≤H2≤7mm. For example, H2 can be set to 4mm, 4.5mm, 5mm, 5.5mm, 6mm, 6.5mm, 7mm, etc.

[0174] Specifically, when H2 is less than 4mm, the volume of the second annular groove 324 is small, resulting in a relatively small amount of lubricating oil stored. Under conditions of long-term operation or high-load operation of the compressor, the lubricating oil is easily depleted, leading to insufficient lubrication. When H2 is greater than 7mm, although the larger second annular groove 324 can store more lubricating oil, this may also lead to uneven distribution of lubricating oil within the second annular groove 324. During compressor operation, the lubricating oil may accumulate at the bottom or in localized areas within the second annular groove 324, failing to be effectively and evenly distributed axially to the parts requiring lubrication.

[0175] Furthermore, referring to Figure 5, the minimum thickness T2 between the side of the second vortex tooth 331 located near the eccentric bearing hole 332 and the eccentric bearing hole 332 in this embodiment (as shown in Figure 5) satisfies the relationship: T2≥1.5mm. For example, T2 can be set to 1.5mm, 1.6mm, 1.8mm, 1.9mm, 2mm, 2.2mm, 2.4mm, 2.5mm, etc.

[0176] Specifically, since the moving scroll plate 33 is a solid structure, it has high strength and rigidity, enabling it to withstand greater pressure without easily deforming. In contrast, the second scroll tooth 331, being too thin, is prone to deformation. In this embodiment, the minimum thickness T2 between the side of the second scroll tooth 331 closest to the eccentric bearing hole 332 and the eccentric bearing hole 332 satisfies the relationship: T2 ≥ 1.5 mm. This ensures the structural strength of the second scroll tooth 331, prevents deformation during compressor operation, and effectively improves the reliability and stability of the compressor.

[0177] Furthermore, in this embodiment, the cross-sectional area of ​​the first bearing portion 322 gradually decreases along the direction away from the eccentric segment 312, and the minimum thickness T3 of the side of the first bearing portion 322 away from the eccentric segment 312 (as shown in Figure 25) satisfies the relationship: T3≥1.5mm. For example, T3 can be set to 1.5mm, 1.6mm, 1.8mm, 1.9mm, 2mm, 2.2mm, 2.4mm, 2.5mm, etc.

[0178] Specifically, since the stationary vortex disk 32 in this embodiment has a first bearing portion 322 and a first bearing hole 323, the first bearing portion 322 sleeves the stationary vortex disk 32 on the side of the first shaft segment 311 near the eccentric segment 312 through the first bearing hole 323. After the stationary vortex disk 32 is installed, the side of the first bearing portion 322 near the eccentric segment 312 will be subjected to load, which will cause the first shaft segment 311 to tilt in the first bearing hole 323. As a result, stress concentration is likely to occur in the load-bearing part of the first shaft segment 311 away from the eccentric segment 312, leading to wear of the first shaft segment 311 and the first bearing portion 322. Therefore, in this embodiment, the minimum thickness T3 of the side of the first bearing portion 322 away from the eccentric section 312 is set to be greater than or equal to 1.5 mm. This reduces the structural strength of the side of the first bearing portion 322 away from the eccentric section 312, thereby allowing the first bearing portion 322 to gradually deform under load and better fit the first shaft section 311, effectively improving stress concentration and enhancing the reliability and stability of the bearing.

[0179] Further, referring to Figures 21 and 22, in this embodiment, the eccentric segment 312 near the end of the second shaft segment 313 or the end of the second shaft segment 313 away from the eccentric segment 312 is provided with a thrust surface 315.

[0180] Specifically, the thrust surface 315 can effectively position the crankshaft 31 axially. During the operation of the compressor, the crankshaft 31 will be subjected to various axial forces, such as the axial force generated by the moving scroll 33 or the bracket 34 when it is working. This axial force is transmitted to the crankshaft 31 through the eccentric section 312 or the second shaft section 313. In this embodiment, a thrust surface 315 is provided at the end of the eccentric section 312 near the second shaft section 313 or at the end of the second shaft section 313 away from the eccentric section 312. These thrust surfaces 315 can directly bear these axial forces, avoid stress concentration, and thus protect the crankshaft 31 and other related components from damage caused by excessive local axial forces, effectively ensuring the reliability of the compressor.

[0181] Furthermore, in this embodiment, the cross-sectional area S of the thrust surface 315 (the area of ​​the cross-section obtained by cutting the thrust surface 315 along a direction perpendicular to the axis of the crankshaft 31) satisfies the following relationship: 45mm 2 ≤S≤85mm 2 For example, D can be set to 45mm 2 50mm 2 55mm 2 60mm 2 65mm 2 70mm 2 75mm 2 80mm 2 85mm 2 wait.

[0182] Specifically, when S is less than 45mm 2 When the cross-sectional area of ​​the thrust surface 315 is small, it is not conducive to the uniform transmission of axial force, which may lead to force concentration in a local area and failure to effectively distribute the axial force to the entire thrust surface 315, thus reducing the reliability of the compressor; when S is greater than 85mm 2 At that time, the cross-sectional area of ​​the thrust surface 315 was too large, which increased the amount of material used in the thrust surface 315 and increased the manufacturing cost of the compressor.

[0183] Furthermore, the crankshaft 31 in this embodiment includes a ductile iron crankshaft with a tensile strength greater than or equal to 500 MPa, such as 500 MPa, 600 MPa, 700 MPa, 800 MPa, 900 MPa, 1000 MPa, etc. Specifically, due to the good wear resistance and vibration damping properties of ductile iron, using it as the material for the crankshaft 31 can reduce the noise and vibration of the pump assembly 30 and the compressor, effectively ensuring the smooth operation of the compressor and improving its reliability. At the same time, the tensile strength of the ductile iron crankshaft greater than or equal to 500 MPa not only improves the load-bearing capacity of the crankshaft 31 and effectively improves its reliability, but also reduces the use of cast iron material, thus lowering the manufacturing cost of the crankshaft 31.

[0184] Furthermore, in this embodiment, the outer surface of the crankshaft 31 is treated with phosphating, or a combination of phosphating and molybdenum treatment, or a diamond-like carbon (DLC) film. Specifically, since the crankshaft 31 is subjected to a large radial load, it has certain strength requirements. When the outer surface of the crankshaft 31 is phosphating, a phosphating film is formed on the surface of the crankshaft 31. This film has a low coefficient of friction and can effectively reduce wear between the crankshaft 31 and other components. When the outer surface of the crankshaft 31 is treated with both phosphating and molybdenum treatment, i.e., molybdenum treatment is performed on the basis of phosphating, a composite film containing molybdenum can be formed on the surface of the crankshaft 31. Since molybdenum has good wear resistance and anti-galling properties, this composite film can better protect the crankshaft 31 under high load and high speed conditions. When the outer surface of the crankshaft 31 is treated with a diamond-like carbon (DLC) film, the surface of the crankshaft 31 has excellent wear resistance. During the operation of the compressor, the DLC film can protect the surface of the crankshaft 31, reduce the wear of the crankshaft 31, and extend the service life of the crankshaft 31.

[0185] Furthermore, the crankshaft 31 in this embodiment includes a low-carbon steel crankshaft, wherein the carbon content of the low-carbon steel crankshaft is less than or equal to 0.6%.

[0186] Specifically, in this embodiment, the crankshaft 31 is made of low-carbon steel with a carbon content of less than or equal to 0.6%, such as 20Cr or 40Cr. This ensures that the crankshaft 31 has good toughness and impact resistance, effectively absorbing and resisting various impact forces, thus ensuring that the crankshaft 31 can still operate normally under long-term impact loads and effectively improving the reliability of the compressor. At the same time, the outer peripheral surface of the crankshaft 31 undergoes surface hardening treatments such as high-frequency quenching, carburizing, nitriding, or diamond-like carbon (DLC) coating, so that the surface hardness of the crankshaft 31 reaches HRC45 or higher.

[0187] It should be noted that 20Cr and 40Cr are Chinese standard steel grades, HRC is Rockwell hardness, and HRC45 means that the Rockwell hardness is 45.

[0188] Furthermore, in this embodiment, the surface hardness of the crankshaft 31 is greater than or equal to 45 HRC. This setting increases the surface hardness of the crankshaft 31, reduces the wear rate of the crankshaft 31, and extends the service life of the crankshaft 31 and related components.

[0189] Furthermore, in this embodiment, when the temperature of the lubricating oil is 40°C, the kinematic viscosity γ of the lubricating oil satisfies the following relationship: 50 mm 2 / s≤γ≤80mm 2 / s, for example, γ can be set to 50mm 2 / s, 55mm 2 / s, 60mm 2 / s, 65mm 2 / s, 70mm 2 / s, 75mm 2 / s, 80mm 2 / s etc.

[0190] Specifically, when γ is less than 50mm 2 At a speed of γ / s, the kinematic viscosity of the lubricating oil is low, and its adhesion to the surface of the components is weakened. This prevents the formation of a sufficiently thick oil film at the mating point between the crankshaft 31 and the pump body assembly 30, increasing the friction between them and leading to accelerated wear. When γ is greater than 80 mm... 2 At a speed of / s, the kinematic viscosity of the lubricating oil is high, and the lubricating oil cannot be delivered to the various parts that need lubrication in a timely manner, which reduces the reliability and energy efficiency of the compressor.

[0191] Furthermore, in this embodiment, the amount of lubricating oil injected, G, satisfies the following relationship: 200mL≤G≤350mL. For example, G can be set to 200mL, 220mL, 240mL, 260mL, 280mL, 300mL, 320mL, 340mL, 350mL, etc.

[0192] Specifically, when G is less than 200mL, the amount of lubricating oil is too small, which prevents the lubricating oil from fully covering all the surfaces of the parts that need lubrication, increasing the wear between the parts; when G is greater than 350mL, the amount of lubricating oil is too large, which increases the stirring resistance when the compressor is running, thereby consuming additional electrical energy and reducing the energy efficiency and reliability of the compressor.

[0193] Further, referring to Figure 1, the compressor in this embodiment also includes a liquid reservoir 90. The housing 10 has an air inlet 11 and an air outlet 12. The air inlet 11 is connected to the liquid reservoir 90 and the compression chamber 301, and the air outlet 12 is connected to the accommodating chamber 101 and the outside. The liquid storage volume V of the liquid reservoir 90 satisfies the relationship 300mL≤V≤500mL. For example, V can be set to 300mL, 350mL, 400mL, 450mL, 500mL, etc.

[0194] Specifically, the compressor is one of the core components of an air conditioning system, and its operation requires the participation of refrigerant. The receiver 90 can store a certain amount of liquid refrigerant. During the operation of the air conditioning system, when the refrigerant flow fluctuates or the compressor's suction demand suddenly increases, the receiver 90 can promptly provide sufficient refrigerant to replenish the system, ensuring the stable operation of the compressor.

[0195] During the start-up phase of the air conditioning system, the compressor needs sufficient refrigerant to establish a normal refrigeration cycle. When V is less than 300mL, the volume of the receiver 90 is too small, and the amount of refrigerant stored is limited, which may not meet the compressor's need for rapid gas intake. When V is greater than 500mL, the volume of the receiver 90 is too large, which increases material and manufacturing costs, resulting in a lower cost-effectiveness of the compressor.

[0196] Furthermore, referring to Figure 1, the pump body assembly 30 in this embodiment also includes a cross slip ring 35, which is installed between the moving scroll plate 33 and the bracket 34. This arrangement facilitates the limiting of the moving scroll plate 33, thereby preventing the moving scroll plate 33 from rotating.

[0197] The compressor of this application will be described in detail below with reference to specific embodiments.

[0198] Example 1

[0199] The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. Referring to Table 1, with the width W1 of the first support fitting part 40 being 35 mm, the width W2 of the second support fitting part 60 being 20 mm, and the width W3 of the third support fitting part 70 being 20 mm, when the outer diameter D1 of the first shaft section is 15 mm, the outer diameter D2 of the eccentric section is 18 mm, and the outer diameter D3 of the second shaft section is 13 mm, the compressor's energy efficiency is 100%, and the compressor has high reliability.

[0200] Example 2

[0201] The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. Referring to Table 1, with the width W1 of the first support fitting part 40 being 35 mm, the width W2 of the second support fitting part 60 being 20 mm, and the width W3 of the third support fitting part 70 being 20 mm, when the outer diameter D1 of the first shaft section is 13 mm, the outer diameter D2 of the eccentric section is 16 mm, and the outer diameter D3 of the second shaft section is 11 mm, the compressor's energy efficiency is 102%, and the compressor's reliability is generally acceptable.

[0202] Example 3

[0203] The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. Referring to Table 1, with the width W1 of the first support fitting part 40 being 35 mm, the width W2 of the second support fitting part 60 being 20 mm, and the width W3 of the third support fitting part 70 being 20 mm, when the outer diameter D1 of the first shaft section is 11 mm, the outer diameter D2 of the eccentric section is 14 mm, and the outer diameter D3 of the second shaft section is 9 mm, the compressor's energy efficiency is 103%, and the compressor's reliability is generally acceptable.

[0204] Comparative Example 1

[0205] The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. Referring to Table 1, with the width W1 of the first support fitting part 40 being 35 mm, the width W2 of the second support fitting part 60 being 20 mm, and the width W3 of the third support fitting part 70 being 20 mm, when the outer diameter D1 of the first shaft section is 16 mm, the outer diameter D2 of the eccentric section is 20 mm, and the outer diameter D3 of the second shaft section is 15 mm, the compressor's energy efficiency is 98%, and the compressor has high reliability.

[0206] Comparative Example 2

[0207] The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. Referring to Table 1, under the conditions that the width W1 of the first support mating part 40 is 35 mm, the width W2 of the second support mating part 60 is 20 mm, and the width W3 of the third support mating part 70 is 20 mm, when the outer diameter D1 of the first shaft section is 10 mm, the outer diameter D2 of the eccentric section is 13 mm, and the outer diameter D3 of the second shaft section is 8 mm, the compressor's energy efficiency is 104%, and the compressor's reliability is low. Table 1: Influence of D1, D2, and D3 on the compressor's energy efficiency and reliability.

[0208] Note: The width of the first support mating part is 35mm, the width of the second support mating part is 20mm, and the width of the third support mating part is 20mm.

[0209] As can be seen from the above embodiments, by limiting the outer diameter D1 of the first shaft segment 311 to satisfy the relationship: 11mm≤D1≤15mm, the outer diameter D2 of the eccentric segment 312 to satisfy the relationship: 14mm≤D2≤18mm, and the outer diameter of the second shaft segment 313 to satisfy the relationship: 9mm≤D3≤13mm, this application can not only ensure that the energy efficiency of the compressor is greater than or equal to 100%, but also effectively ensure the reliability of the compressor.

[0210] Example 4

[0211] The first shaft segment 311 has a first support fitting portion 40 that mates with the first bearing hole 323 or the second bearing hole 342; the eccentric segment 312 has a second support fitting portion 60 that mates with the eccentric bearing hole 332; and the second shaft segment 313 has a third support fitting portion 70 that mates with the first bearing hole 323 or the second bearing hole 342. Referring to Table 2, under the conditions that the outer diameter of the first shaft segment 311 is 13 mm, the outer diameter of the eccentric segment 312 is 16 mm, and the outer diameter of the second shaft segment 313 is 11 mm, when the width W1 of the first support fitting portion 40 is 35 mm, the width W2 of the second support fitting portion 60 is 18 mm, and the width W3 of the third support fitting portion 70 is 18 mm, the compressor's energy efficiency is 100%, and the compressor has good reliability.

[0212] Example 5

[0213] The first shaft segment 311 has a first support fitting portion 40 that mates with the first bearing hole 323 or the second bearing hole 342; the eccentric segment 312 has a second support fitting portion 60 that mates with the eccentric bearing hole 332; and the second shaft segment 313 has a third support fitting portion 70 that mates with the first bearing hole 323 or the second bearing hole 342. Referring to Table 2, under the conditions that the outer diameter of the first shaft segment 311 is 13 mm, the outer diameter of the eccentric segment 312 is 16 mm, and the outer diameter of the second shaft segment 313 is 11 mm, when the width W1 of the first support fitting portion 40 is 25 mm, the width W2 of the second support fitting portion 60 is 15 mm, and the width W3 of the third support fitting portion 70 is 15 mm, the compressor's energy efficiency is 101%, and the compressor's reliability is generally acceptable.

[0214] Example 6

[0215] The first shaft segment 311 has a first support fitting portion 40 that mates with the first bearing hole 323 or the second bearing hole 342; the eccentric segment 312 has a second support fitting portion 60 that mates with the eccentric bearing hole 332; and the second shaft segment 313 has a third support fitting portion 70 that mates with the first bearing hole 323 or the second bearing hole 342. Referring to Table 2, under the conditions that the outer diameter of the first shaft segment 311 is 13 mm, the outer diameter of the eccentric segment 312 is 16 mm, and the outer diameter of the second shaft segment 313 is 11 mm, when the width W1 of the first support fitting portion 40 is 22 mm, the width W2 of the second support fitting portion 60 is 12 mm, and the width W3 of the third support fitting portion 70 is 10 mm, the compressor's energy efficiency is 101%, and the compressor's reliability is generally acceptable.

[0216] Comparative Example 3

[0217] The first shaft segment 311 has a first support fitting portion 40 that mates with the first bearing hole 323 or the second bearing hole 342; the eccentric segment 312 has a second support fitting portion 60 that mates with the eccentric bearing hole 332; and the second shaft segment 313 has a third support fitting portion 70 that mates with the first bearing hole 323 or the second bearing hole 342. Referring to Table 2, under the conditions that the outer diameter of the first shaft segment 311 is 13 mm, the outer diameter of the eccentric segment 312 is 16 mm, and the outer diameter of the second shaft segment 313 is 11 mm, when the width W1 of the first support fitting portion 40 is 40 mm, the width W2 of the second support fitting portion 60 is 20 mm, and the width W3 of the third support fitting portion 70 is 20 mm, the compressor's energy efficiency is 98%, and the compressor has good reliability.

[0218] Comparative Example 4

[0219] The first shaft segment 311 has a first support fitting portion 40 that mates with the first bearing hole 323 or the second bearing hole 342; the eccentric segment 312 has a second support fitting portion 60 that mates with the eccentric bearing hole 332; and the second shaft segment 313 has a third support fitting portion 70 that mates with the first bearing hole 323 or the second bearing hole 342. Referring to Table 2, under the conditions that the outer diameter of the first shaft segment 311 is 13 mm, the outer diameter of the eccentric segment 312 is 16 mm, and the outer diameter of the second shaft segment 313 is 11 mm, when the width W1 of the first support fitting portion 40 is 20 mm, the width W2 of the second support fitting portion 60 is 10 mm, and the width W3 of the third support fitting portion 70 is 9 mm, the compressor's energy efficiency is 101%, and the compressor's reliability is low.

[0220] As can be seen from the above embodiments, by limiting the width W1 of the first support mating part 40 to satisfy the relationship: 22mm≤W1≤35mm, the width W2 of the second support mating part 60 to satisfy the relationship: 12mm≤W2≤18mm, and the width W3 of the third support mating part 70 to satisfy the relationship: 10mm≤W3≤18mm, this application can not only ensure that the energy efficiency of the compressor is greater than or equal to 100%, but also effectively ensure the reliability of the compressor.

[0221] Table 2 shows the impact of W1, W2, and W3 on the energy efficiency and reliability of the compressor.

[0222] Note: The outer diameter of the first shaft section is 13mm, the outer diameter of the eccentric section is 16mm, and the outer diameter of the second shaft section is 11mm.

[0223] On the other hand, this application also provides an air conditioning system that includes the compressor described above. Therefore, this air conditioning system includes all the technical effects of the compressor described above. Since the technical effects of the compressor used in the air conditioning system have already been described in detail above, they will not be repeated here.

[0224] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0225] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0226] The above are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A compressor for use in an air conditioning system, the air conditioning system comprising a refrigerant, an evaporator, a condenser, a throttling device, and the compressor, wherein the rated cooling capacity CC of the air conditioning system satisfies the relationship: 2500W ≤ CC ≤ 3700W, and the compressor comprises a vertical variable frequency scroll compressor, characterized in that, The compressor also includes: The housing (10) has a receiving cavity (101), and the bottom of the receiving cavity (101) is provided with an oil storage space (102) for storing lubricating oil. The motor (20) is disposed in the accommodating cavity (101), and the motor (20) includes a rotor (21) and a stator (22) sleeved on the outer periphery of the rotor (21); A pump body assembly (30) is disposed within the receiving cavity (101) and near the bottom of the receiving cavity (101). The pump body assembly (30) includes a crankshaft (31), a stationary scroll plate (32), a moving scroll plate (33), and a bracket (34). The crankshaft (31) is rotatably disposed within the receiving cavity (101) and passes through the motor (20) and the stationary scroll plate. (32) The moving scroll plate (33) and the bracket (34), the stationary scroll plate (32) is provided with a first scroll tooth (321) on the side near the moving scroll plate (33), the moving scroll plate (33) is provided with a second scroll tooth (331) that meshes with the first scroll tooth (321), the first scroll tooth (321) and the second scroll tooth (331) mesh to form a compression cavity (301); The crankshaft (31) includes a first shaft segment (311), an eccentric segment (312), and a second shaft segment (313). The first shaft segment (311), the eccentric segment (312), and the second shaft segment (313) are arranged sequentially along the axial direction of the crankshaft (31). The first shaft segment (311) is located on the side of the eccentric segment (312) closer to the motor (20), and the second shaft segment (313) is located on the side of the eccentric segment (312) away from the motor (20). On one side of the stationary scroll plate (32), a first bearing portion (322) is provided on the side opposite to the moving scroll plate (33), the first bearing portion (322) has a first bearing hole (323), the moving scroll plate (33) has an eccentric bearing hole (332) through which the eccentric section (312) passes, and a second bearing portion (341) is provided on the side opposite to the moving scroll plate (33), the second bearing portion (341) has a second bearing hole (342); The outer diameter D1 of the first shaft segment (311) satisfies the following relationship: 11mm≤D1≤15mm; The outer diameter D2 of the eccentric section (312) satisfies the following relationship: 14mm≤D2≤18mm; The outer diameter D3 of the second shaft segment (313) satisfies the following relationship: 9mm≤D3≤13mm.

2. The compressor for use in an air conditioning system according to claim 1, characterized in that, The outer diameter D1 of the first shaft segment (311) satisfies the following relationship: 12.5mm≤D1≤13.5mm; The outer diameter D3 of the second shaft segment (313) satisfies the following relationship: 9.5mm≤D3≤11.5mm.

3. The compressor for use in an air conditioning system according to claim 1, characterized in that, The outer diameter D4 of the stator (22) satisfies the following relationship: 96mm≤D4≤104mm.

4. The compressor for use in an air conditioning system according to claim 1, characterized in that, The outer diameter D5 of the moving scroll disk (33) satisfies the following relationship: 78mm≤D5≤82mm.

5. The compressor for use in an air conditioning system according to claim 1, characterized in that, The first shaft segment (311) has a first support fitting portion (40) that mates with the first bearing hole (323) or the second bearing hole (342). Along the axial direction of the crankshaft (31), the width W1 of the first support fitting portion (40) satisfies the relationship: 22mm ≤ W1 ≤ 35mm; and / or, The first shaft segment (311) has a first support fitting part (40) that mates with the first bearing hole (323) or the second bearing hole (342). Along the axial direction of the crankshaft (31), the maximum distance L1 between the end of the first support fitting part (40) away from the eccentric segment (312) and the end of the eccentric segment (312) close to the first shaft segment (311) satisfies the relationship: 30mm≤L1≤45mm.

6. The compressor for use in an air conditioning system according to claim 5, characterized in that, The crankshaft (31) is provided with an oil supply channel (314), which extends from the end of the second shaft section (313) toward the direction close to the first shaft section (311); The outer surface of the first support fitting part (40) is provided with a first oil groove (41), the first oil groove (41) is connected to the oil supply channel (314) through a first oil hole (42), the first shaft section (311) is provided with an annular groove (325), the annular groove (325) is located between the first support fitting part (40) and the eccentric section (312) and is arranged around the first shaft section (311) in the circumferential direction, the first oil groove (41) extends along the axial direction of the crankshaft (31) and extends from the first support fitting part (40) to the annular groove (325).

7. The compressor for use in an air conditioning system according to claim 6, characterized in that, In the projection along the direction from the first shaft segment (311) to the eccentric segment (312), the projections of the first shaft segment (311) and the eccentric segment (312) both include circles. A first ray (50) is drawn with the center of the circle of the first shaft segment (311) as the endpoint and passing through the center of the circle of the eccentric segment (312). The first ray (50) is 0° and the direction of rotation and angle increase of the crankshaft (31) is counterclockwise. The first oil groove (41) is disposed on the outer surface of the first shaft segment (311) and is located between 0° and 180° and between 270° and 360°.

8. The compressor for use in an air conditioning system according to claim 6, characterized in that, The first support mating part (40) includes two support sections (43) arranged sequentially along the axial direction of the crankshaft (31). The outer surfaces of the two support sections (43) each have the first oil groove (41). Among the two support sections (43), the width of the support section (43) arranged closer to the eccentric section (312) along the axial direction of the crankshaft (31) is greater than the width of the support section (43) arranged further away from the eccentric section (312) along the axial direction of the crankshaft (31).

9. The compressor for use in an air conditioning system according to claim 8, characterized in that, The outer surface of the first support mating part (40) is provided with a first annular groove (45), the first annular groove (45) is arranged around the first shaft segment (311) in the circumferential direction, and the first annular groove (45) is located between the two support segments (43) to at least store lubricating oil.

10. The compressor for use in an air conditioning system according to claim 1, characterized in that, The eccentric section (312) has a second support fitting part (60) that mates with the eccentric bearing hole (332). Along the axial direction of the crankshaft (31), the width W2 of the second support fitting part (60) satisfies the relationship: 12mm≤W2≤18mm.

11. The compressor for use in an air conditioning system according to claim 1, characterized in that, The eccentric section (312) has a second support fitting part (60) that mates with the eccentric bearing hole (332). The center of the width of the second support fitting part (60) along the axial direction of the crankshaft (31) is located at half the height of the second scroll tooth part (331) along the axial direction of the crankshaft (31) and between the end face of the moving scroll disk (33) facing away from the second scroll tooth part (331).

12. The compressor for use in an air conditioning system according to claim 1, characterized in that, The second shaft segment (313) has a third support fitting part (70) that mates with the first bearing hole (323) or the second bearing hole (342). Along the axial direction of the crankshaft (31), the width W3 of the third support fitting part (70) satisfies the relationship: 10mm≤W3≤18mm.

13. The compressor for use in an air conditioning system according to claim 1, characterized in that, The first shaft segment (311) has a first support fitting part (40) that mates with the first bearing hole (323) or the second bearing hole (342), and the outer surface of the first support fitting part (40) is provided with a first oil groove (41); The eccentric section (312) has a second support fitting part (60) that mates with the eccentric bearing hole (332). The second support fitting part (60) has a second oil groove (61). The second oil groove (61) is disposed on the outer surface of the second support fitting part (60) along the axial direction of the crankshaft (31), and the second oil groove (61) is connected to the first oil groove (41) through an annular groove (325).

14. The compressor for use in an air conditioning system according to claim 13, characterized in that, The crankshaft (31) is provided with an oil supply channel (314), which extends from the end of the second shaft section (313) toward the direction close to the first shaft section (311); The eccentric section (312) has a second support fitting part (60) that mates with the eccentric bearing hole (332). The second support fitting part (60) has a third oil groove (62). The third oil groove (62) is located on the outer surface of the second support fitting part (60) and extends along the axial direction of the crankshaft (31). The width of the third oil groove (62) along the axial direction of the crankshaft (31) is smaller than the width of the second support fitting part (60) along the axial direction of the crankshaft (31). The third oil groove (62) communicates with the oil supply channel (314) through the second oil hole (63).

15. The compressor for use in an air conditioning system according to claim 14, characterized in that, The second oil groove (61) has a first groove edge (611) and a second groove edge (612) arranged opposite to each other along the circumference of the crankshaft (31), and the included angle between the line connecting the first groove edge (611) and the center of the eccentric segment (312) and the line connecting the second groove edge (612) and the center of the eccentric segment (312) is θ1; The third oil groove (62) has a third groove edge (621) and a fourth groove edge (622) arranged opposite to each other along the circumference of the crankshaft (31). The angle between the line connecting the third groove edge (621) and the center of the eccentric segment (312) and the line connecting the fourth groove edge (622) and the center of the eccentric segment (312) is θ2. Among them, θ1 and θ2 satisfy the relationship that θ1+θ2≥30°.

16. The compressor for use in an air conditioning system according to claim 14, characterized in that, In the projection along the direction from the first shaft segment (311) to the eccentric segment (312), the projections of the first shaft segment (311) and the eccentric segment (312) both include circles. A first ray (50) is drawn with the center of the circle of the first shaft segment (311) as the endpoint and passing through the center of the circle of the eccentric segment (312). The first ray (50) is 0° and counterclockwise is the direction of rotation of the crankshaft (31) and the direction of increasing angle. The second oil groove (61) and the third oil groove (62) are disposed on the outer surface of the eccentric segment (312) and are located between 90° and 360°.

17. The compressor for use in an air conditioning system according to claim 1, characterized in that, The crankshaft (31) is provided with an oil supply channel (314), which extends from the end of the second shaft section (313) toward the direction close to the first shaft section (311); The second shaft segment (313) has a third support fitting part (70) that mates with the first bearing hole (323) or the second bearing hole (342). The outer surface of the third support fitting part (70) is provided with a fourth oil groove (71). The fourth oil groove (71) is connected to the oil supply channel (314) through a third oil hole (72). The width of the fourth oil groove (71) along the axial direction of the crankshaft (31) is smaller than the width of the third support fitting part (70) along the axial direction of the crankshaft (31).

18. The compressor for use in an air conditioning system according to claim 17, characterized in that, In the projection along the direction from the first shaft segment (311) to the eccentric segment (312), the projections of the first shaft segment (311) and the eccentric segment (312) both include circles. A first ray (50) is drawn with the center of the circle of the first shaft segment (311) as the endpoint and passing through the center of the circle of the eccentric segment (312). The first ray (50) is 0° and the direction of rotation and angle increase of the crankshaft (31) is counterclockwise. The fourth oil groove (71) is disposed on the outer surface of the second shaft segment (313) and is located between 0° and 210° and between 270° and 360°.

19. The compressor for use in an air conditioning system according to any one of claims 1 to 18, characterized in that, The first shaft segment (311) has a first support fitting part (40) that mates with the first bearing hole (323) or the second bearing hole (342), and the outer surface of the first support fitting part (40) is provided with a first oil groove (41); The eccentric section (312) has a second support fitting part (60) that mates with the eccentric bearing hole (332), and the outer surface of the second support fitting part (60) is provided with a second oil groove (61) and a third oil groove (62); The second shaft segment (313) has a third support fitting part (70) that mates with the first bearing hole (323) or the second bearing hole (342), and the outer surface of the third support fitting part (70) is provided with a fourth oil groove (71); The first oil tank (41), the second oil tank (61), the third oil tank (62), and the fourth oil tank (71) all include a straight oil tank (100) or a spiral oil tank (110), and the cross-sectional area of ​​the first oil tank (41), the second oil tank (61), the third oil tank (62), and the fourth oil tank (71) is greater than or equal to 0.35 mm. 2 .

20. The compressor for use in an air conditioning system according to claim 1, characterized in that, The first shaft segment (311) has a first fitting clearance with the first bearing hole (323) or the second bearing hole (342). Along the radial direction of the crankshaft (31), the width A1 of the first fitting clearance satisfies the relationship: 0.015mm ≤ A1 ≤ 0.04mm; and / or, A second fitting clearance exists between the eccentric section (312) and the eccentric bearing hole (332) along the radial direction of the crankshaft (31), and the width A2 of the second fitting clearance satisfies the following relationship: 0.015mm ≤ A2 ≤ 0.04mm; and / or, The second shaft segment (313) has a third fitting clearance with the first bearing hole (323) or the second bearing hole (342). Along the radial direction of the crankshaft (31), the width A3 of the third fitting clearance satisfies the relationship: 0.015mm≤A3≤0.04mm.

21. The compressor for use in an air conditioning system according to claim 1, characterized in that, The first shaft segment (311) has a first support fitting portion (40) that mates with the first bearing hole (323) or the second bearing hole (342), and the outer diameter of the first support fitting portion (40) gradually decreases in the direction away from the eccentric segment (312).

22. The compressor for use in an air conditioning system according to claim 21, characterized in that, The taper C of the first support fitting part (40) satisfies the following relationship: C = H1 / L2, and 1 / 2000 ≤ C ≤ 1 / 1000, where H1 is the maximum distance between the first support fitting part (40) and the inner wall of the first bearing hole (323) or the second bearing hole (342), and L2 is the height of the first support fitting part (40) along the axial direction of the crankshaft (31).

23. The compressor for use in an air conditioning system according to claim 1, characterized in that, A bushing (80) is provided between the eccentric bearing hole (332) of the moving scroll disk (33) and the crankshaft (31).

24. The compressor for use in an air conditioning system according to claim 23, characterized in that, The bushing (80) is made of at least one of polytetrafluoroethylene, carbon, and aluminum alloy.

25. The compressor for use in an air conditioning system according to claim 1, characterized in that, A second annular groove (324) is provided on the side of the stationary vortex disk (32) or the support (34) near the eccentric section (312). The second annular groove (324) is arranged around the outer periphery of the first bearing hole (323) along the circumference of the stationary vortex disk (32) or around the outer periphery of the second bearing hole (342) along the circumference of the support (34), and is spaced apart from the first bearing hole (323) or the second bearing hole (342).

26. The compressor for use in an air conditioning system according to claim 25, characterized in that, Along the radial direction of the crankshaft (31), the minimum thickness T1 between the side of the second annular groove (324) near the first bearing hole (323) and the first bearing hole (323), or between the side of the second annular groove (324) near the second bearing hole (342) and the second bearing hole (342), satisfies the following relationship: T1 ≥ 1.5 mm; and / or, Along the radial direction of the crankshaft (31), the width D6 of the second annular groove (324) satisfies the relationship: 1.5mm ≤ D6 ≤ 2.5mm; and / or, Along the axial direction of the crankshaft (31), the height H2 of the second annular groove (324) satisfies the relationship: 4mm≤H2≤7mm.

27. The compressor for use in an air conditioning system according to claim 1, characterized in that, The minimum thickness T2 between the side of the second vortex tooth (331) located near the eccentric bearing hole (332) away from the eccentric bearing hole (332) and the eccentric bearing hole (332) satisfies the relationship: T2≥1.5mm.

28. The compressor for use in an air conditioning system according to claim 1, characterized in that, Along the direction away from the eccentric segment (312), the cross-sectional area of ​​the first bearing portion (322) gradually decreases, and the minimum thickness T3 of the first bearing portion (322) on the side away from the eccentric segment (312) satisfies the relationship: T3≥1.5mm.

29. The compressor for use in an air conditioning system according to claim 1, characterized in that, A thrust surface (315) is provided at one end of the eccentric segment (312) near the second shaft segment (313) or at one end of the second shaft segment (313) away from the eccentric segment (312).

30. The compressor for use in an air conditioning system according to claim 29, characterized in that, The cross-sectional area S of the thrust surface (315) satisfies the following relationship: 45mm 2 ≤S≤85mm 2 .

31. The compressor for use in an air conditioning system according to claim 1, characterized in that, The crankshaft (31) comprises a ductile iron crankshaft having a tensile strength greater than or equal to 500 MPa; and / or, The outer surface of the crankshaft (31) is treated with phosphating or molybdenum plating or diamond-like carbon film; and / or, The crankshaft (31) comprises a low-carbon steel crankshaft, wherein the carbon content of the low-carbon steel crankshaft is less than or equal to 0.6%; and / or, The surface hardness of the crankshaft (31) is greater than or equal to 45 HRC.

32. The compressor for use in an air conditioning system according to claim 1, characterized in that, When the temperature of the lubricating oil is 40°C, the kinematic viscosity γ of the lubricating oil satisfies the following relationship: 50 mm 2 / s≤γ≤80mm 2 / s; and / or, The amount of lubricating oil injected, G, satisfies the following relationship: 200mL≤G≤350mL.

33. The compressor for use in an air conditioning system according to claim 1, characterized in that, The compressor also includes a liquid reservoir (90), and the housing (10) has an air inlet (11) and an air outlet (12). The air inlet (11) is connected to the liquid reservoir (90) and the compression chamber (301), and the air outlet (12) is connected to the accommodating chamber (101) and the outside. The liquid storage volume V of the liquid reservoir (90) satisfies the relationship 300mL≤V≤500mL.

34. An air conditioning system, characterized in that, The air conditioning system includes the compressor used in the air conditioning system as described in any one of claims 1 to 33.

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