Compressor applied to air conditioning system and air conditioning system

Abstract

The application discloses a compressor applied to an air conditioning system and the air conditioning system. The compressor further comprises a shell, a motor and a pump body assembly. The pump body assembly comprises a crankshaft, a static scroll disc, a dynamic scroll disc, a sealing element, an anti-rotation element and a bracket. The static scroll disc is provided with a first scroll tooth portion, the dynamic scroll disc is provided with a second scroll tooth portion, and the first scroll tooth portion and the second scroll tooth portion are engaged to form a compression cavity. An oil supply channel is arranged on the crankshaft. The side, away from the crankshaft, of the sealing element is surrounded by the static scroll disc, the dynamic scroll disc and the bracket to form a first pressure space. The side, close to the crankshaft, of the sealing element is surrounded by the dynamic scroll disc and the bracket to form a second pressure space. The static scroll disc, the dynamic scroll disc and the bracket are provided with a medium portion. When the dynamic scroll disc rotates and moves, the medium portion periodically transports lubricating oil from the second pressure space to the first pressure space. The application can solve the problem that the oil inlet amount of the scroll compressor in the prior art is difficult to control.

Description

Technical Field

[0001] 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

[0002] 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 and reliability have a significant impact on the overall performance of the air conditioner.

[0003] Existing compressors typically include rotary compressors and scroll compressors. Among them, scroll compressors have higher energy efficiency than rotary compressors due to their higher volumetric efficiency and lower leakage. However, existing scroll compressors generally adopt a pump-top structure, meaning the pump body is placed above the motor. This results in only one bearing supporting the crankshaft in the pump body, requiring an additional bearing below the motor to support the crankshaft. Furthermore, because the pump body is far from the bottom oil sump, a positive displacement oil pump is needed for forced oil supply, and bushings are generally required at the bearings to ensure reliable operation. This makes the scroll compressor structure more complex and more expensive. However, this forced oil supply method is prone to over-supply, causing a large amount of lubricating oil to enter the pump body, increasing the compressor's oil discharge and adversely affecting its energy efficiency and reliability. Summary of the Invention

[0004] 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 that scroll compressors in the prior art have difficulty controlling the oil intake of the pump body.

[0005] 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 Q of the air conditioning system satisfies the relationship: 2500W ≤ Q ≤ 3700W. The compressor includes a vertical variable frequency scroll compressor, and further includes:

[0006] The housing has a receiving cavity, and the bottom of the receiving cavity is provided with an oil storage space for storing lubricating oil;

[0007] 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;

[0008] A pump body assembly is disposed within the accommodating cavity and positioned closer to the bottom of the accommodating cavity than the motor. The pump body assembly includes a crankshaft, a stationary scroll plate, a moving scroll plate, a seal, an anti-rotation component, 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, the seal, the anti-rotation component, and the bracket. The stationary scroll plate has a first scroll tooth on its 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.

[0009] The crankshaft includes a first shaft segment, an eccentric segment, and a second shaft segment. The first shaft segment, the eccentric segment, and the second shaft segment are arranged sequentially along the axial direction of the crankshaft. The first shaft segment is located on the side of the eccentric segment closer to the motor, and the second shaft segment is located on the side of the eccentric segment away from the motor. The motor is sleeved on the first shaft segment. A first bearing portion is provided on the side of the stationary scroll plate away from the moving scroll plate. The first bearing portion has a first bearing hole. The moving scroll plate has an eccentric bearing hole through which the eccentric segment passes. A second bearing portion is provided on the side of the bracket away from the moving scroll plate. The second bearing portion has a second bearing hole. The stationary scroll plate is sleeved on the first shaft segment or the second shaft segment through the first bearing hole. The bracket is sleeved on the second shaft segment or the first shaft segment through the second bearing hole.

[0010] The crankshaft is provided with an oil supply channel. The seal and the anti-rotation component are both disposed between the moving scroll and the bracket. The anti-rotation component is disposed on the side of the seal away from the crankshaft. The side of the seal away from the crankshaft, together with the stationary scroll, the moving scroll, and the bracket, forms a first pressure space. The side of the seal close to the crankshaft, together with the moving scroll and the bracket, forms a second pressure space. A medium is disposed on one of the stationary scroll, the moving scroll, and the bracket. When the moving scroll rotates and translates, the medium periodically delivers the lubricating oil from the second pressure space to the first pressure space.

[0011] Furthermore, 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 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,

[0015] 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.

[0016] Furthermore, the diameter D4 of the oil supply channel satisfies the following relationship: D4≤6mm.

[0017] Furthermore, the minimum operating frequency F1 of the compressor satisfies the relationship: F1≤15Hz.

[0018] Furthermore, the amount of lubricating oil V injected into the compressor satisfies the following relationship: 200mL≤V≤350mL.

[0019] Furthermore, a first sealing groove is provided on the side of the bracket near the moving scroll plate. The first sealing groove is arranged circumferentially around the second bearing hole, and the sealing element is provided within the first sealing groove. The medium portion is provided on the side of the moving scroll plate near the bracket. The medium portion has a first end near the eccentric bearing hole and a second end away from the eccentric bearing hole. The first end extends to the eccentric bearing hole or is spaced a predetermined distance from the eccentric bearing hole; or...

[0020] The moving scroll plate is provided with a second sealing groove on the side near the bracket. The second sealing groove is arranged around the circumference of the eccentric bearing hole and has the sealing element inside. The bracket is provided with a medium part on the side near the moving scroll plate. The medium part has a third end near the second bearing hole and a fourth end away from the second bearing hole. The third end extends to the second bearing hole or is spaced a predetermined distance from the second bearing hole.

[0021] Furthermore, the distance between the central axis of the first shaft segment and the central axis of the eccentric segment is r0, and the length of the projection of the medium portion along the crankshaft axis is L0;

[0022] A first sealing groove is provided on a side of the bracket close to the orbiting scroll, the sealing member is arranged in the first sealing groove, a distance between a side of the sealing member close to a crankshaft and a central axis of the crankshaft is r1, a distance between a side of the sealing member away from the crankshaft and the central axis of the crankshaft is r2, the medium part is provided on a side of the orbiting scroll close to the bracket, a distance between an end of a first end of the medium part and a central axis of an eccentric bearing hole is R1;

[0023] wherein, when r0, L0, r1, r2 and R1 satisfy the relational expressions: R1 + r0 < r1, and R1 + L0 - r0 < r2 < R1 + L0 + r0, the orbiting scroll performs revolution translation such that the first end of the medium part is always communicated with the second pressure space, and a second end of the medium part is periodically communicated with the first pressure space.

[0024] further, a distance between a central axis of the first shaft section and a central axis of the eccentric section is r0, a length of a projection of the medium part along an axial direction of the crankshaft is L0;

[0025] A first sealing groove is provided on a side of the bracket close to the orbiting scroll, the sealing member is arranged in the first sealing groove, a distance between a side of the sealing member close to a crankshaft and a central axis of the crankshaft is r1, a distance between a side of the sealing member away from the crankshaft and the central axis of the crankshaft is r2, the medium part is provided on a side of the orbiting scroll close to the bracket, a distance between an end of a first end of the medium part and a central axis of an eccentric bearing hole is R1;

[0026] wherein, when r0, L0, r1, r2 and R1 satisfy the relational expressions: r2 < R1 + L0 - r0, and R1 - r0 < r1 < R1 + r0, the orbiting scroll performs revolution translation such that the first end of the medium part is periodically communicated with the second pressure space, and a second end of the medium part is always communicated with the first pressure space.

[0027] further, a distance between a central axis of the first shaft section and a central axis of the eccentric section is r0, a length of a projection of the medium part along an axial direction of the crankshaft is L0;

[0028] A first sealing groove is provided on a side of the bracket close to the orbiting scroll, the sealing member is arranged in the first sealing groove, a distance between a side of the sealing member close to a crankshaft and a central axis of the crankshaft is r1, a distance between a side of the sealing member away from the crankshaft and the central axis of the crankshaft is r2, the medium part is provided on a side of the orbiting scroll close to the bracket, a distance between an end of a first end of the medium part and a central axis of an eccentric bearing hole is R1;

[0029] wherein when r0, L0, r1, r2 and R1 satisfy the relational expression: R1+L0-r0<r2<R1+L0+r0 and R1-r0<r1<R1+r0, the orbiting scroll performs rotary translation so that the first end of the medium portion periodically communicates with the second pressure space, and the second end of the medium portion periodically communicates with the first pressure space.

[0030] further, the distance between the central axis of the first shaft section and the central axis of the eccentric section is r0, and the length of the projection of the medium portion along the axial direction of the crankshaft is L0;

[0031] a second sealing groove is provided on a side of the orbiting scroll close to the bracket, the sealing member is provided in the second sealing groove, a distance between a side of the sealing member close to the crankshaft and a central axis of the crankshaft is r3, a distance between a side of the sealing member far from the crankshaft and the central axis of the crankshaft is r4, the medium portion is provided on a side of the bracket close to the orbiting scroll, and a distance between an end portion of a third end of the medium portion and a central axis of the second bearing hole is R2;

[0032] wherein when r0, L0, r3, r4 and R2 satisfy the relational expression: R2<r3-r0 and r4-r0<R2+L0<r4+r0, the orbiting scroll performs rotary translation so that the third end of the medium portion always communicates with the second pressure space, and a fourth end of the medium portion periodically communicates with the first pressure space.

[0033] further, the distance between the central axis of the first shaft section and the central axis of the eccentric section is r0, and the length of the projection of the medium portion along the axial direction of the crankshaft is L0;

[0034] a second sealing groove is provided on a side of the orbiting scroll close to the bracket, the sealing member is provided in the second sealing groove, a distance between a side of the sealing member close to the crankshaft and a central axis of the crankshaft is r3, a distance between a side of the sealing member far from the crankshaft and the central axis of the crankshaft is r4, the medium portion is provided on a side of the bracket close to the orbiting scroll, and a distance between an end portion of a third end of the medium portion and a central axis of the second bearing hole is R2;

[0035] wherein when r0, L0, r3, r4 and R2 satisfy the relational expression: r4+r0<R2+L0 and r3-r0<R2<r3+r0, the orbiting scroll performs rotary translation so that the third end of the medium portion periodically communicates with the second pressure space, and the fourth end of the medium portion always communicates with the first pressure space.

[0036] Further, the distance between the central axis of the first shaft segment and the central axis of the eccentric segment is r0, and the projection length of the medium portion along the axial direction of the crankshaft is L0;

[0037] A second sealing groove is provided on a side of the orbiting scroll close to the support, the sealing member is disposed in the second sealing groove, the distance between a side of the sealing member close to the crankshaft and the central axis of the crankshaft is r3, the distance between a side of the sealing member away from the crankshaft and the central axis of the crankshaft is r4, the medium portion is provided on a side of the support close to the orbiting scroll, and the distance between an end of the third end of the medium portion and the central axis of the second bearing hole is R2;

[0038] Wherein, when r0, L0, r3, r4 and R2 satisfy the relational expressions: r4-r0<R2+L0<r4+r0 and r3-r0<R2<r3+r0, the orbiting scroll performs orbiting translation so that the third end of the medium portion periodically communicates with the second pressure space, and the fourth end of the medium portion periodically communicates with the first pressure space.

[0039] Further, the medium portion comprises an oil groove, a first oil hole or a second oil hole;

[0040] When the medium portion comprises the oil groove, the oil groove is provided on an end surface of the orbiting scroll close to the support or an end surface of the support close to the orbiting scroll, and extends along the radial direction of the crankshaft; or,

[0041] When the medium portion comprises the first oil hole, the first oil hole is provided on a side of the orbiting scroll close to the support or a side of the support close to the orbiting scroll, the first oil hole comprises a first hole segment, a second hole segment and a third hole segment, the first hole segment and the second hole segment both extend along the axial direction of the crankshaft, the first hole segment is located on a side of the sealing member close to the crankshaft, the second hole segment is located on a side of the sealing member away from the crankshaft, the third hole segment extends along the radial direction of the crankshaft and opposite ends of the third hole segment respectively communicate with the first hole segment and the second hole segment; or,

[0042] When the medium portion comprises the second oil hole, the second oil hole is provided on a side of the orbiting scroll close to the support and extends along the axial direction of the crankshaft, and is disposed close to the sealing member, or the second oil hole is provided on a side of the support close to the orbiting scroll and extends along the axial direction of the crankshaft, and is disposed close to the sealing member.

[0043] Further, the depth H1 of the oil groove along the axial direction of the crankshaft satisfies the relational expression: H1≥0.05mm; and / or,

[0044] The minimum diameter D5 of the first oil hole satisfies the following relationship: D5 ≥ 0.1 mm; and / or,

[0045] The depth H2 of the second oil hole along the crankshaft axis satisfies the following relationship: H2≥0.05mm.

[0046] Furthermore, the medium includes a third oil hole, which is disposed on the stationary scroll or the moving scroll. The third oil hole includes a fourth segment, a fifth segment, and a sixth segment. The fourth segment and the fifth segment both extend axially along the crankshaft, and the sixth segment extends radially along the crankshaft, with its opposite ends communicating with the fourth segment and the fifth segment, respectively.

[0047] Furthermore, the stationary scroll plate is provided with the third oil hole, wherein the fourth hole segment and the fifth hole segment both extend along the axial direction of the crankshaft and extend in the same direction. The fourth hole segment is closer to the crankshaft than the fifth hole segment. The opening of the fourth hole segment communicates with the second pressure space. The opening of the fifth hole segment is located at the sealing surface between the moving scroll plate and the stationary scroll plate. When the moving scroll plate rotates and translates, the opening of the fourth hole segment is always in communication with the second pressure space, and the opening of the fifth hole segment periodically communicates with the first pressure space.

[0048] Furthermore, the stationary scroll plate is provided with the third oil hole, wherein the fourth hole segment and the fifth hole segment both extend along the axial direction of the crankshaft and extend in the same direction. The fourth hole segment is closer to the crankshaft than the fifth hole segment. The opening of the fourth hole segment is located close to the second pressure space, and the opening of the fifth hole segment is connected to the first pressure space. When the moving scroll plate rotates and translates, the opening of the fourth hole segment periodically connects to the second pressure space, and the opening of the fifth hole segment is always connected to the first pressure space.

[0049] Furthermore, the stationary scroll plate is provided with the third oil hole, wherein the fourth hole segment and the fifth hole segment both extend along the axial direction of the crankshaft and extend in the same direction. The fourth hole segment is closer to the crankshaft than the fifth hole segment, and the opening of the fourth hole segment is located close to the second pressure space. The opening of the fifth hole segment is located at the sealing surface between the moving scroll plate and the stationary scroll plate. When the moving scroll plate rotates and translates, the opening of the fourth hole segment periodically communicates with the second pressure space, and the opening of the fifth hole segment periodically communicates with the first pressure space.

[0050] Furthermore, the moving scroll disk is provided with the third oil hole, wherein the fourth hole segment and the fifth hole segment both extend along the axial direction of the crankshaft and extend in opposite directions, the fourth hole segment is closer to the crankshaft than the fifth hole segment, the opening of the fourth hole segment communicates with the second pressure space, and the opening of the fifth hole segment is located at the sealing surface of the moving scroll disk and the stationary scroll disk. When the moving scroll disk rotates and translates, the fourth hole segment is always in communication with the second pressure space, and the opening of the fifth hole segment periodically communicates with the first pressure space.

[0051] Furthermore, the moving scroll disk is provided with the third oil hole, wherein the fourth hole segment and the fifth hole segment both extend along the axial direction of the crankshaft and extend in opposite directions, the fourth hole segment is closer to the crankshaft than the fifth hole segment, the opening of the fourth hole segment is located close to the second pressure space, and the opening of the fifth hole segment is located at the sealing surface of the moving scroll disk and the stationary scroll disk. When the moving scroll disk rotates and translates, the fourth hole segment periodically communicates with the second pressure space, and the opening of the fifth hole segment periodically communicates with the first pressure space.

[0052] Furthermore, the minimum diameter D6 of the third oil hole satisfies the following relationship: D6≥0.1mm.

[0053] Furthermore, the mediating section includes at least one; when the mediating section includes multiple mediating sections, the multiple mediating sections are circumferentially spaced on the stationary scroll plate, the moving scroll plate, or the support along the crankshaft, and the multiple mediating sections include at least one of an oil groove, a first oil hole, a second oil hole, and a third oil hole.

[0054] On the other hand, this application also provides an air conditioning system, which includes the compressor described above for use in air conditioning systems.

[0055] Compared to existing compressors, this application incorporates a media unit on one of the stationary scroll, moving scroll, and support. This media unit has an on / off function. When the compressor starts operating, the moving scroll rotates and translates under the rotation of the crankshaft, causing a change in the position of the media unit relative to the seal. This allows the media unit to move between the first and second pressure spaces, ultimately achieving periodic oil supply to both spaces. This configuration allows control over the amount of oil supplied from the second pressure space to the first pressure space, preventing insufficient oil supply, effectively ensuring compressor performance and reliability, and extending the compressor's service life. Attached Figure Description

[0056] 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:

[0057] Figure 1 This is a cross-sectional view of the compressor disclosed in an embodiment of this application;

[0058] Figure 2 This is a cross-sectional view of the pump body assembly (oil sump located on the moving scroll plate, seal located on the bracket) disclosed in the embodiments of this application;

[0059] Figure 3 The appendices disclosed in the embodiments of this application Figure 2 Enlarged view of region A in the middle;

[0060] Figure 4 This is a cross-sectional view of the pump body assembly (the first oil hole is located on the moving scroll plate and the seal is located on the bracket) disclosed in the embodiments of this application;

[0061] Figure 5 The appendices disclosed in the embodiments of this application Figure 4 Enlarged view of region B in the middle;

[0062] Figure 6 This is a cross-sectional view of the pump body assembly (oil sump located on the bracket, seal located on the moving scroll plate) disclosed in the embodiments of this application;

[0063] Figure 7 The appendices disclosed in the embodiments of this application Figure 6 Enlarged view of region C in the middle;

[0064] Figure 8 This is a cross-sectional view of the pump body assembly (the first oil hole is located on the bracket and the seal is located on the moving scroll plate) disclosed in the embodiments of this application;

[0065] Figure 9 The appendices disclosed in the embodiments of this application Figure 8 Enlarged view of region D in the middle;

[0066] Figure 10 This is a cross-sectional view of the pump body assembly (the third oil hole is located on the stationary vortex disk) disclosed in the embodiments of this application;

[0067] Figure 11 This is a cross-sectional view of the pump body assembly (the third oil hole is located on the moving scroll plate) disclosed in the embodiments of this application;

[0068] Figure 12 This is a schematic diagram of the flow of lubricating oil when the media part is located in the moving scroll plate or the support, as disclosed in the embodiments of this application;

[0069] Figure 13This is a schematic diagram of the flow of lubricating oil when the media section is located in the stationary vortex disk, as disclosed in the embodiments of this application.

[0070] Figure 14 This is a cross-sectional view of the crankshaft disclosed in an embodiment of this application;

[0071] Figure 15 This is a cross-sectional view of the pump body assembly disclosed in an embodiment of this application;

[0072] Figure 16 This is a cross-sectional view of the stationary vortex disk disclosed in the embodiments of this application;

[0073] Figure 17 This is a schematic diagram of the structure of the stent disclosed in the embodiments of this application;

[0074] Figure 18 This is a cross-sectional view of the moving scroll disk disclosed in the embodiments of this application;

[0075] Figure 19 This is a schematic diagram of the structure of the oil tank located on the moving scroll disk disclosed in the embodiments of this application;

[0076] Figure 20 This is a schematic diagram showing the dimensions of the oil tank when it is located on the moving scroll plate, as disclosed in the embodiments of this application.

[0077] Figure 21 This is a schematic diagram showing the dimensions of the oil tank when it is located on the support, as disclosed in the embodiments of this application;

[0078] Figure 22 This is a schematic diagram of the structure disclosed in this application when the oil tank is located on the moving scroll plate and the seal is located on the support.

[0079] Figure 23 This is a schematic diagram of a structure in which the first pressure space and the second pressure space are periodically connected, as disclosed in the embodiments of this application.

[0080] Figure 24 This is a schematic diagram of a second type of structure in which the first pressure space and the second pressure space are periodically connected, as disclosed in an embodiment of this application.

[0081] Figure 25 This is a schematic diagram of a third type of structure in which the first pressure space and the second pressure space are periodically connected when the second oil hole is in the first position, as disclosed in an embodiment of this application.

[0082] Figure 26 This is a schematic diagram of a third type of structure in which the first pressure space and the second pressure space are periodically connected when the second oil hole is in the second position, as disclosed in an embodiment of this application.

[0083] Figure 27 This is a schematic diagram of the structure disclosed in this application when the oil tank is located in the bracket and the seal is located in the moving scroll plate;

[0084] Figure 28 This is a schematic diagram of a fourth type of structure in which the first pressure space and the second pressure space are periodically connected, as disclosed in the embodiments of this application.

[0085] Figure 29 This is a schematic diagram of a fifth type of structure in which the first pressure space and the second pressure space are periodically connected, as disclosed in the embodiments of this application.

[0086] Figure 30 This is a schematic diagram of a sixth type of structure in which the first pressure space and the second pressure space are periodically connected when the oil tank is in the third position, as disclosed in the embodiments of this application.

[0087] Figure 31 This is a schematic diagram of a sixth type of structure in which the first pressure space and the second pressure space are periodically connected when the oil tank is in the fourth position, as disclosed in the embodiments of this application.

[0088] The above figures include the following reference numerals:

[0089] 10. Housing; 101. Receiving cavity; 102. Oil storage space; 20. Motor; 21. Rotor; 22. Stator;

[0090] 30. Pump body assembly; 31. Crankshaft; 311. First shaft section; 3111. First support mating part; 312. Eccentric section; 313. Second shaft section; 314. Oil supply channel; 32. Stationary scroll plate; 321. First scroll tooth section; 322. First bearing section; 323. First bearing hole; 33. Moving scroll plate; 331. Second scroll tooth section; 332. Eccentric bearing hole; 333. Second sealing groove; 34. Seal; 35. Anti-rotation component; 36. Bracket; 361. Second Bearing section; 362, second bearing hole; 363, first sealing groove; 40, medium section; 401, first end; 402, second end; 403, third end; 404, fourth end; 41, oil groove; 42, first oil hole; 421, first hole section; 422, second hole section; 423, third hole section; 43, second oil hole; 44, third oil hole; 441, fourth hole section; 442, fifth hole section; 443, sixth hole section; 50, first pressure space; 60, second pressure space. Detailed Implementation

[0091] 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.

[0092] 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.

[0093] 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.

[0094] See Figures 1 to 31 As shown, according to an embodiment of the 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 Q of the air conditioning system satisfies the relationship: 2500W ≤ Q ≤ 3700W. The compressor includes a vertical variable frequency scroll compressor, and the compressor also includes a casing 10, a motor 20, and a pump assembly 30. Exemplarily, Q in this embodiment can be set to 2500W, 2600W, 2700W, 2800W, 2900W, 3000W, 3100W, 3200W, 3300W, 3400W, 3500W, 3600W, 3700W, etc.

[0095] Specifically, 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 closer to the bottom of the receiving cavity 101 than the motor 20, and the pump body assembly 30 includes a crankshaft 31, a stationary scroll plate 32, a moving scroll plate 33, a seal 34, and an anti-rotation component. The crankshaft 31 is rotatably disposed within the accommodating cavity 101, and passes through the motor 20, the stationary scroll 32, the moving scroll 33, the seal 34, the anti-rotation component 35, and the bracket 36. 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.

[0096] The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. The first shaft section 311, eccentric section 312, and second shaft section 313 are arranged sequentially along the axial direction of the crankshaft 31. The first shaft section 311 is located on the side of the eccentric section 312 closer to the motor 20, and the second shaft section 313 is located on the side of the eccentric section 312 away from the motor 20. The motor 20 is fitted onto the first shaft section 311. 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 361 is provided on the side of the bracket 36 away from the moving scroll plate 33. The second bearing portion 361 has a second bearing hole 362. The stationary scroll plate 32 is fitted onto the first shaft section 311 through the first bearing hole 323. 11 or the second shaft segment 313, the bracket 36 is sleeved on the second shaft segment 313 or the first shaft segment 311 through the second bearing hole 362; the crankshaft 31 is provided with an oil supply channel 314, the seal 34 and the anti-rotation component 35 are both provided between the moving scroll 33 and the bracket 36, and the anti-rotation component 35 is provided on the side of the seal 34 away from the crankshaft 31, the side of the seal 34 away from the crankshaft 31, together with the stationary scroll 32, the moving scroll 33 and the bracket 36, forms a first pressure space 50, the side of the seal 34 close to the crankshaft 31, together with the moving scroll 33 and the bracket 36, forms a second pressure space 60, and one of the stationary scroll 32, the moving scroll 33 and the bracket 36 is provided with a medium part 40, when the moving scroll 33 rotates and translates, the medium part 40 periodically delivers lubricating oil from the second pressure space 60 to the first pressure space 50. It is worth noting that in this embodiment, the oil supply channel 314 is connected to the oil storage space 102.

[0097] It is understood that in this embodiment, the stationary scroll 32 may be sleeved on the first shaft segment 311 through the first bearing hole 323, and the bracket 36 may be sleeved on the second shaft segment 313 through the second bearing hole 362; alternatively, the stationary scroll 32 may be sleeved on the second shaft segment 313 through the first bearing hole 323, and the bracket 36 may be sleeved on the first shaft segment 311 through the second bearing hole 362. (The appendix of this embodiment is missing.) Figure 1 The diagram shows the situation where the stationary vortex disk 32 is sleeved on the first shaft section 311 through the first bearing hole 323 and the bracket 36 is sleeved on the second shaft section 313 through the second bearing hole 362.

[0098] In this embodiment, during the actual manufacturing of the compressor, both the motor 20 and the pump assembly 30 can be installed within the accommodating cavity 101, with the first shaft segment 311 located on the side of the eccentric segment 312 closer to the motor 20, and the second shaft segment 313 located on the side of the eccentric segment 312 farther from the motor 20. Since the moving scroll plate 33 is fitted onto the eccentric segment 312 through the eccentric bearing hole 332, and the motor 20 is driven by the crankshaft 31, when the motor 20 drives the crankshaft 31 to rotate, it can drive the eccentric segment 312 to rotate, thereby driving the moving scroll plate 33 to rotate synchronously, and further driving the stationary scroll plate 32 to rotate relative to the moving scroll plate 33 to compress the refrigerant entering the compression chamber. Meanwhile, since the stationary scroll plate 32 in this embodiment has a first bearing portion 322 and the bracket 36 has a second bearing portion 361, and the pump body assembly 30 is closer to the bottom of the receiving cavity 101 than the motor 20, i.e., the compressor adopts a bottom-mounted pump body assembly 30 structure, the presence of the first bearing portion 322 and the second bearing portion 361 can support the crankshaft 31, thus eliminating the need for an additional bearing on the other side of the motor 20 to support the crankshaft 31. Furthermore, the first bearing portion 322 and the second bearing portion 361 are closer to the lubricating oil at the bottom of the receiving cavity 101, thus ensuring reliable compressor operation without the need for additional bushings. The overall structure is simple and the manufacturing cost is low.

[0099] Furthermore, since the seal 34 in this embodiment is disposed between the moving scroll plate 33 and the bracket 36, the side of the seal 34 away from the crankshaft 31 (i.e., the outer side of the seal 34) can be surrounded by the stationary scroll plate 32, the moving scroll plate 33 and the bracket 36 to form a first pressure space 50, and the side of the seal 34 close to the crankshaft 31 (i.e., the inner side of the seal 34) can be surrounded by the moving scroll plate 33 and the bracket 36 to form a second pressure space 60. As a result, the back side of the moving scroll plate 33 (i.e., the side of the moving scroll plate 33 away from the stationary scroll plate 32) floats under the combined action of the first pressure space 50 and the second pressure space 60.

[0100] Combined again Figure 1As shown, in this embodiment, the lubricating oil is transported from the bottom of the mounting cavity to the oil supply channel 314 under the action of pressure difference, and then delivered to the outside of the crankshaft 31 through the oil hole communicating with the oil supply channel 314. It then flows downwards along the side wall of the crankshaft 31 between the moving scroll 33 and the bracket 36. This lubricating oil is supplied from the second pressure space 60 to the first pressure space 50 via the medium part 40 to lubricate the moving scroll 33, the anti-rotation component 35, and the bracket 36. At this time, if the first pressure space 50 and the second pressure space 60 are always in a state of... In the connected state, during the rotation and translation of the moving scroll 33, the lubricating oil will continuously flow from the second pressure space 60 into the first pressure space 50 through the medium part 40, increasing the amount of lubricating oil entering the space. Excess lubricating oil will enter the compression chamber formed by the stationary scroll 32 and the moving scroll 33 from the first pressure space 50, instead of flowing back to the oil storage space 102 at the bottom of the mounting chamber. As the compressor continues to operate, the lubricating oil in the oil storage space 102 is easily reduced, which will affect the performance and service life of the compressor. Therefore, in this embodiment, a medium 40 is provided on the stationary scroll plate 32, the moving scroll plate 33, or the bracket 36. As the moving scroll plate 33 rotates and moves, the position of the medium 40 relative to the seal 34 also changes accordingly. This allows the first pressure space 50 and the second pressure space 60 to be periodically supplied with oil. In this way, the amount of oil supplied from the second pressure space 60 to the first pressure space 50 can be controlled, preventing insufficient oil supply to the compressor, effectively ensuring the performance and reliability of the compressor, and extending the service life of the compressor to a certain extent.

[0101] In other words, compared with the compressors in the prior art, this application provides a medium section 40 on one of the three components: the stationary scroll plate 32, the moving scroll plate 33, and the bracket 36. The medium section 40 has an on / off function. When the compressor starts working, the moving scroll plate 33 rotates and translates under the rotation of the crankshaft 31, thereby causing the position of the medium section 40 relative to the seal 34 to change, so that the medium section 40 can move between the first pressure space 50 and the second pressure space 60, ultimately realizing the periodic oil supply to the first pressure space 50 and the second pressure space 60. With this configuration, the amount of oil supplied from the second pressure space 60 to the first pressure space 50 can be controlled, thereby preventing insufficient oil supply to the compressor, effectively ensuring the performance and reliability of the compressor, and extending the service life of the compressor.

[0102] Specifically, in this embodiment, the sealing element 34 includes a sealing ring; the anti-rotation element 35 includes a cross slip ring, which facilitates the limiting of the moving scroll plate 33. Optionally, in other embodiments of this application, the anti-rotation element 35 can also be set as a ball coupling or a cylindrical pin coupling, etc. Any other variation under the concept of this application is within the protection scope of this application.

[0103] Furthermore, in this embodiment, the outer diameter D1 of the first shaft segment 311 (e.g.) Figure 14 As shown, the following relationship is satisfied: 11mm≤D1≤15mm. For example, D1 can be set to 11mm, 11.5mm, 12mm, 12.5mm, 13mm, 13.5mm, 14mm, 14.5mm, 15mm, etc.

[0104] Specifically, regarding the bearing reliability of the compressor, under constant load and lubrication conditions, a larger crankshaft diameter (31) leads to higher reliability. However, increasing the crankshaft diameter increases frictional energy consumption, resulting in reduced compressor efficiency. Therefore, while ensuring reliability, a smaller crankshaft diameter (31) results in higher compressor efficiency. Based on this, for compressors with a cooling capacity ranging from 2500W to 3700W, an outer diameter (D1) of the first shaft section (311) between 11mm and 15mm effectively ensures compressor reliability while maintaining optimal efficiency. When D1 is less than 11mm, the structural strength of the first shaft section (311) is low, making it prone to bending and deformation during high-speed compressor operation, potentially leading to breakage. When the outer diameter (D1) is greater than 15mm, the weight and manufacturing cost of the crankshaft (31) increase, hindering the lightweight and miniaturized design of the compressor.

[0105] Furthermore, in this embodiment, the outer diameter D2 of the eccentric segment 312 (e.g.) Figure 14 As shown, the following relationship is satisfied: 14mm≤D2≤18mm. For example, D2 can be set to 14mm, 14.5mm, 15mm, 15.5mm, 16mm, 16.5mm, 17mm, 17.5mm, 18mm, etc.

[0106] Specifically, regarding the bearing reliability of the compressor, under constant load and lubrication conditions, a larger crankshaft diameter (31) leads to higher reliability. However, increasing the crankshaft diameter increases frictional energy consumption, resulting in reduced compressor efficiency. Therefore, while ensuring reliability, a smaller crankshaft diameter (31) results in higher compressor efficiency. Based on this, for compressors with a cooling capacity ranging from 2500W to 3700W, an outer diameter (D2) of eccentric section (312) between 14mm and 18mm effectively ensures compressor reliability while maintaining optimal efficiency. When D2 is less than 14mm, the structural strength of eccentric section (312) is low, making it difficult for it to support the moving scroll plate (33), thus affecting the proper fit between the moving scroll plate (33) and the stationary scroll plate (32). When the outer diameter (D2) of eccentric section (312) is greater than 18mm, the mass of eccentric section (312) increases, leading to increased inertia of the entire crankshaft (31), negatively impacting compressor performance.

[0107] Furthermore, in this embodiment, the outer diameter D3 of the second shaft segment 313 (e.g.) Figure 14 As shown, the following relationship is satisfied: 9mm≤D3≤13mm. For example, D3 can be set to 9mm, 9.5mm, 10mm, 10.5mm, 11mm, 11.5mm, 12mm, 12.5mm, 13mm, etc.

[0108] Specifically, regarding the bearing reliability of the compressor, under constant load and lubrication conditions, a larger crankshaft diameter (31) leads to higher reliability. However, increasing the crankshaft diameter increases frictional energy consumption, resulting in reduced compressor efficiency. Therefore, while ensuring reliability, a smaller crankshaft diameter (31) results in higher compressor efficiency. Based on this, for compressors with a cooling capacity ranging from 2500W to 3700W, an outer diameter (D3) of the second shaft section (313) within the range of 9mm to 13mm effectively ensures compressor reliability while maintaining optimal energy efficiency. When the outer diameter D3 of the second shaft section 313 is less than 9mm, the structural strength of the second shaft section 313 is low, which means that the second shaft section 313 is not enough to support the weight of the bracket 36 and other auxiliary components. During the operation of the compressor, the bracket 36 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.

[0109] Further, see Figure 15As shown, in this embodiment, the first shaft segment 311 has a first support fitting portion 3111 that mates with the first bearing hole 323 or the second bearing hole 362. Along the axial direction of the crankshaft 31, the width W1 of the first support fitting portion 3111 is (e.g., ...). Figure 15 As shown, the following relationship is satisfied: 22mm ≤ W1 ≤ 35mm. For example, W1 can be set to 22mm, 24mm, 26mm, 28mm, 30mm, 32mm, 34mm, 35mm, etc. It is understood that in this embodiment, the first shaft segment 311 can cooperate with the first bearing hole 323 to form the first support fitting part 3111, or it can cooperate with the second bearing hole 362 to form the first support fitting part 3111. The appendix of this embodiment... Figure 15 The diagram shows the situation when the first shaft segment 311 is engaged with the first bearing hole 323.

[0110] Specifically, a larger support width of the first support mating part 3111 results in a larger bearing surface, thereby reducing the surface pressure on the first bearing part 322 or the second bearing part 361. This, in turn, reduces the likelihood that the first bearing part 322 or the second bearing part 361 will be prone to wear, thus reducing the reliability of the compressor. However, an excessively large contact area between the first bearing part 322 and the first shaft section 311, or between the second bearing part 361 and the first shaft section 311, will lead to increased frictional energy consumption, which is detrimental to the compressor's energy efficiency. Specifically, when W1 is less than 22mm, the fit length between the first bearing part 322 and the first shaft section 311, or the fit length between the second bearing part 361 and the first shaft section 311, is shortened, reducing the contact area between the first bearing part 322 and the first shaft section 311, or the contact area between the second bearing part 361 and the first shaft section 311. This leads to an increase in the pressure per unit area, further exacerbating the wear on the first bearing part 322 or the second bearing part 361, and reducing the reliability of the compressor operation. When W1 is greater than 35mm, the contact area between the first bearing part 322 and the first shaft section 311 is too large, or the fit length between the second bearing part 361 and the first shaft section 311 is too large. The excessively large contact area between the crankshaft 361 and the first shaft segment 311 increases the friction between the first bearing portion 322 and the first shaft segment 311 or between the second bearing portion 361 and the first shaft segment 311. This causes wear on both the first bearing portion 322 and the first shaft segment 311, or the second bearing portion 361 and the first shaft segment 311, reducing the reliability of the compressor operation. At the same time, the excessively wide first support mating portion 3111 increases the mass of the crankshaft 31, thereby increasing the moment of 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.

[0111] Further, see Figure 15As shown, in this embodiment, the first shaft segment 311 has a first support fitting portion 3111 that mates with the first bearing hole 323 or the second bearing hole 362. Along the axial direction of the crankshaft 31, the maximum distance L1 between the end of the first support fitting portion 3111 away from the eccentric segment 312 and the end of the eccentric segment 312 near the first shaft segment 311 (e.g., ...) Figure 15 As shown, the following relationship is satisfied: 30mm≤L1≤45mm. For example, L1 can be set to 30mm, 32mm, 34mm, 36mm, 38mm, 40mm, 42mm, 44mm, 45mm, etc.

[0112] 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 for the 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 3111. 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 3111 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 3111 will be greater, which will generate a larger load on the first bearing part 322 or the second bearing part 361, reducing the reliability of the first bearing part 322 or the second bearing part 361. Based on this, this embodiment shortens the lever arm by ensuring that L1 satisfies the relationship: 30mm≤L1≤45mm, thereby reducing the torque acting on the first support mating part 3111, and further reducing the load on the first bearing part 322 or the second bearing part 361, effectively improving the reliability of the first bearing part 322 or the second bearing part 361. Specifically, according to the torque formula, when L1 is less than 30mm, the force needs to be increased accordingly to generate the same torque. In the compressor, to maintain a certain torque to drive the crankshaft 31 to rotate, a smaller lever arm means that the motor 20 needs to output a larger force, leading to motor overload and shortening the motor 20's service life. When L1 is greater than 45mm, the torque is too large, causing the crankshaft 31 to bend and deform during rotation, reducing the compressor's reliability.

[0113] Furthermore, in this embodiment, the diameter D4 of the oil supply channel 314 (e.g.) Figure 14As shown, the following relationship must be satisfied: D4 ≤ 6mm. For example, D4 ​​can be set to 6mm, 5.5mm, 5mm, 4.5mm, 4mm, 3.5mm, 3mm, 2.5mm, 2mm, 1.5mm, 1mm, etc. Specifically, due to the diameter limitations of the first shaft segment 311 and the second shaft segment 313, and to ensure that the first shaft segment 311 and the second shaft segment 313 have sufficient thickness to guarantee the safety of the crankshaft 31, the diameter of the oil supply channel 314 is limited, making it difficult to increase the diameter of the oil supply channel 314. When D4 is greater than 6mm, the remaining thickness of the crankshaft 31 is relatively thin, reducing the structural strength of the crankshaft 31, thereby reducing the reliability and stability of the crankshaft 31.

[0114] Furthermore, in this embodiment, the minimum operating frequency F1 of the compressor satisfies the relationship: F1 ≤ 15Hz. For example, F1 can be set to 15Hz, 14Hz, 13Hz, 12Hz, 11Hz, 10Hz, 9Hz, 8Hz, 7Hz, 6Hz, 5Hz, etc. Specifically, in order to meet the comfort and energy-saving requirements of the air conditioning system, thereby forming multi-condition adjustment and allowing the air conditioning system to operate within a wider range, the minimum operating frequency F1 of the compressor will be less than or equal to 15Hz.

[0115] Furthermore, in this embodiment, the amount of lubricating oil V injected into the compressor satisfies the following relationship: 200mL≤V≤350mL. For example, V can be set to 200mL, 220mL, 240mL, 260mL, 280mL, 300mL, 320mL, 340mL, 350mL, etc.

[0116] Specifically, considering the operating conditions of air conditioning systems with a cooling capacity ranging from 2500W to 3700W, and to ensure the reliability of lubrication in these systems, the oil level V of the compressor should be between 200mL and 350mL based on the refrigerant charge. After sealing the oil, the oil level in the oil storage space 102 should be near the upper end face of the bracket 36, thus ensuring sufficient oil level during compressor operation. When V is less than 220mL, the lubricating oil level is insufficient, failing to form a sufficiently thick oil film on the components of the pump assembly 30, leading to increased wear on the pump assembly 30 and reduced compressor compression efficiency. When V is greater than 350mL, the lubricating oil level is excessive, increasing the resistance during compressor operation and consequently increasing compressor energy consumption.

[0117] Furthermore, in one embodiment of this application, when the moving scroll plate 33 rotates and translates, the first end 401 of the medium section 40 is always connected to the second pressure space 60, and the second end 402 of the medium section 40 is periodically connected to the first pressure space 50. Considering that the oil level formed after the oil injection of the air conditioning system is limited is low, the required supply height needs to be supplied to the top of the bearing when the first shaft section 311 mates with the first bearing or the second bearing, and the first pressure space 50 forming the back pressure needs to form an intermediate pressure between the suction pressure and the exhaust pressure, so that the moving scroll plate 33 floats upward, and the top of the second scroll tooth 331 and the bottom of the first scroll tooth 321 have good fit, thereby ensuring that the leakage of the pump body assembly 30 is reduced. Meanwhile, considering that the first pressure space 50 contains multiple friction pairs due to structures such as the anti-rotation component 35, good lubrication is required. Furthermore, considering that the pump body assembly 30, in addition to internal lubrication and sealing via air intake and oil transfer, also needs to be connected to the first pressure space 50, this helps to create an intermediate pressure. On the other hand, the lubricating oil in the first pressure space 50 will be sprayed into the pump body assembly 30 with pressure fluctuations, ensuring lubrication and sealing during pump body assembly 30 operation, thereby ensuring efficient compressor operation. Additionally, considering the small diameter of the oil supply channel 314 due to the crankshaft 31's diameter and the low minimum operating frequency of the compressor, a differential pressure oil supply method is preferable without increasing costs. Therefore, this embodiment utilizes the difference between the high pressure at the oil surface (similar to the pressure in the second pressure space 60) and the intermediate pressure in the first pressure space 50, and delivers lubricating oil from the second pressure space 60 to the first pressure space 50 through the oil supply channel 314 and the medium part 40.

[0118] Furthermore, in another embodiment of this application, when the moving scroll plate 33 rotates and translates, the first end 401 of the medium section 40 periodically communicates with the second pressure space 60, and the second end 402 of the medium section 40 is always communicated with the first pressure space 50. Thus, the pressure and the supply of lubricating oil can be adjusted through periodic communication. In another embodiment of this application, when the moving scroll plate 33 rotates and translates, the first end 401 of the medium section 40 periodically communicates with the second pressure space 60, and the second end 402 of the medium section 40 periodically communicates with the first pressure space 50. Thus, the pressure and the supply of lubricating oil can be adjusted through periodic communication.

[0119] Further, see Figures 2 to 5As shown, in this embodiment, the support 36 near the moving scroll plate 33 is provided with a first sealing groove 363. The first sealing groove 363 is arranged circumferentially around the second bearing hole 362, and a sealing element 34 is provided in the first sealing groove 363. The moving scroll plate 33 near the support 36 is provided with a medium portion 40. The medium portion 40 has a first end 401 near the eccentric bearing hole 332 and a second end 402 away from the eccentric bearing hole 332. The first end 401 extends to the eccentric bearing hole 332 or is spaced at a predetermined distance from the eccentric bearing hole 332; or, see Figures 6 to 9 As shown, a second sealing groove 333 is provided on the side of the moving scroll plate 33 near the support 36. The second sealing groove 333 is arranged around the circumference of the eccentric bearing hole 332, and a sealing element 34 is provided in the second sealing groove 333. A medium part 40 is provided on the side of the support 36 near the moving scroll plate 33. The medium part 40 has a third end 403 near the second bearing hole 362 and a fourth end 404 away from the second bearing hole 362. The third end 403 extends to the second bearing hole 362 or is spaced at a predetermined distance from the second bearing hole 362.

[0120] Specifically, see Figure 3 as well as Figure 5 As shown, in one embodiment of this application, a first sealing groove 363 is provided on the side of the support 36 near the moving scroll plate 33. The first sealing groove 363 is arranged circumferentially around the second bearing hole 362, and a sealing element 34 is provided within the first sealing groove 363. A medium part 40 is provided on the side of the moving scroll plate 33 near the support 36. Since the sealing element 34 is provided on the support 36 and the medium part 40 is provided on the moving scroll plate 33, the rotating translational motion of the moving scroll plate 33 will drive the medium part 40 to move, thereby realizing the periodic communication between the first pressure space 50 and the second pressure space 60. See also Figure 7 as well as Figure 9 As shown, in another embodiment of this application, a second sealing groove 333 is provided on the side of the moving scroll plate 33 near the support 36. The second sealing groove 333 is arranged circumferentially around the eccentric bearing hole 332, and a sealing element 34 is provided in the second sealing groove 333. A medium part 40 is provided on the side of the support 36 near the moving scroll plate 33. Since the sealing element 34 is provided on the moving scroll plate 33 and the medium part 40 is provided on the support 36, the moving scroll plate 33 will drive the sealing element 34 to move when it rotates and translates, thereby realizing the periodic communication between the first pressure space 50 and the second pressure space 60.

[0121] Furthermore, in this embodiment, the distance between the central axis of the first shaft segment 311 and the central axis of the eccentric segment 312 is r0 (e.g., Figure 14 As shown), the length of the projection of the media section 40 along the crankshaft 31 axis is L0 (as shown). Figure 19as shown); a side of the bracket 36 close to the orbiting scroll 33 is provided with a first sealing groove 363, a sealing member 34 is arranged in the first sealing groove 363, and the distance between one side of the sealing member 34 close to the crankshaft 31 and the central axis of the crankshaft 31 is r1 (as Figure 20 shown), and the distance between one side of the sealing member 34 away from the crankshaft 31 and the central axis of the crankshaft 31 is r2 (as Figure 20 shown); a side of the orbiting scroll 33 close to the bracket 36 is provided with a medium portion 40, the distance between the end of the first end 401 of the medium portion 40 and the central axis of the eccentric bearing hole 332 is R1 (as Figure 20 shown); wherein when r0, L0, r1, r2 and R1 satisfy the relational expressions: R1+r0<r1 and R1+L0-r0<r2<R1+L0+r0, the orbiting scroll 33 performs orbiting translation so that the first end 401 of the medium portion 40 is always in communication with the second pressure space 60, and the second end 402 of the medium portion 40 is periodically in communication with the first pressure space 50. Illustratively, the medium portion 40 in this embodiment includes an oil groove 41, or a first oil hole 42, or a second oil hole 43. It should be noted that, in this embodiment, "the projection length of the medium portion 40 along the axial direction of the crankshaft 31 is L0" refers to the distance between the first end 401 of the medium portion 40 and the second end 402 of the medium portion 40.

[0122] Specifically, considering that the actual communication condition is related to structural dimensions, this embodiment further defines the dimensions. Wherein when r0, L0, r1, r2 and R1 satisfy the relational expressions: R1+r0<r1 and R1+L0-r0<r2<R1+L0+r0, by virtue of the orbiting motion of the orbiting scroll 33, the medium portion 40 located on the orbiting scroll 33 can move synchronously with the orbiting scroll 33, so that the first end 401 of the medium portion 40 is always in communication with the second pressure space 60, and the second end 402 of the medium portion 40 is periodically in communication with the first pressure space 50. Therefore, it is not necessary to reduce the depth, width or aperture of the oil groove 41, the oil hole and other dimensions, which effectively prevents the flow groove with a smaller size from being blocked by foreign matters, improves the throttling effect of the medium portion 40, and further can control the pressure value in the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50. Meanwhile, this mode makes the medium portion 40 easier to process, more convenient to adjust the pressure and the injection amount of lubricating oil, and ensures the high efficiency and reliability of the compressor operation.

[0123] Further, in this embodiment, the distance between the central axis of the first shaft segment 311 and the central axis of the eccentric segment 312 in this embodiment is r0, and the length of the projection of the medium portion 40 along the axial direction of the crankshaft 31 is L0; a first sealing groove 363 is provided on a side of the bracket 36 close to the orbiting scroll 33, a sealing member 34 is provided in the first sealing groove 363, the distance between a side of the sealing member 34 close to the crankshaft 31 and the central axis of the crankshaft 31 is r1, and the distance between a side of the sealing member 34 away from the crankshaft 31 and the central axis of the crankshaft 31 is r2; a medium portion 40 is provided on a side of the orbiting scroll 33 close to the bracket 36, and the distance between the end of the first end 401 of the medium portion 40 and the central axis of the eccentric bearing hole 332 is R1; wherein when r0, L0, r1, r2 and R1 satisfy the relational expressions: r2 < R1 + L0 - r0 and R1 - r0 < r1 < R1 + r0, the orbiting scroll 33 performs orbiting translation so that the first end 401 of the medium portion 40 periodically communicates with the second pressure space 60, and the second end 402 of the medium portion 40 always communicates with the first pressure space 50. Illustratively, the medium portion 40 in this embodiment includes an oil groove 41, a first oil hole 42 or a second oil hole 43.

[0124] Specifically, considering that the actual communication condition is related to structural dimensions, this embodiment further defines the dimensions. Wherein when r0, L0, r1, r2 and R1 satisfy the relational expressions: R1 + r0 < r1 and R1 + L0 - r0 < r2 < R1 + L0 + r0, relying on the orbiting motion of the orbiting scroll 33, the medium portion 40 located on the orbiting scroll 33 can move synchronously with the orbiting scroll 33, so that the first end 401 of the medium portion 40 periodically crosses the sealing member 34 to periodically communicate with the second pressure space 60, and the second end 402 of the medium portion 40 always communicates with the first pressure space 50. In this way, the pressure value in the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50 can be controlled. Meanwhile, this arrangement makes the medium portion 40 easier to process, and facilitates the adjustment of pressure and the injection amount of lubricating oil, ensuring the high efficiency and reliability of compressor operation.

[0125] Further, in this embodiment, the distance between the central axis of the first shaft section 311 and the central axis of the eccentric section 312 is r0, and the length of the projection of the medium portion 40 along the axial direction of the crankshaft 31 is L0; a first sealing groove 363 is provided on a side of the bracket 36 close to the orbiting scroll 33, a sealing member 34 is provided in the first sealing groove 363, the distance between a side of the sealing member 34 close to the crankshaft 31 and the central axis of the crankshaft 31 is r1, the distance between a side of the sealing member 34 away from the crankshaft 31 and the central axis of the crankshaft 31 is r2, a medium portion 40 is provided on a side of the orbiting scroll 33 close to the bracket 36, and the distance between the end of the first end 401 of the medium portion 40 and the central axis of the eccentric bearing hole 332 is R1; wherein when r0, L0, r1, r2 and R1 satisfy the relational expressions: R1+L0-r0<r2<R1+L0+r0 and R1-r0<r1<R1+r0, the orbiting scroll 33 revolves and translates such that the first end 401 of the medium portion 40 periodically communicates with the second pressure space 60, and the second end 402 of the medium portion 40 periodically communicates with the first pressure space 50. Illustratively, the medium portion 40 in this embodiment includes an oil groove 41, a first oil hole 42 or a second oil hole 43.

[0126] Specifically, considering that the actual communication condition is related to the structural size, this embodiment further defines the size. Wherein when r0, L0, r1, r2 and R1 satisfy the relational expressions: R1+L0-r0<r2<R1+L0+r0 and R1-r0<r1<R1+r0, relying on the revolving motion of the orbiting scroll 33, the medium portion 40 located on the orbiting scroll 33 can move synchronously with the orbiting scroll 33, so that the first end 401 of the medium portion 40 periodically communicates with the second pressure space 60, and the second end 402 of the medium portion 40 periodically communicates with the first pressure space 50. In this way, the pressure value in the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50 can be controlled. Meanwhile, this approach makes the medium portion 40 easier to process, and facilitates adjusting the pressure and the injection amount of lubricating oil, ensuring the high efficiency and reliability of the compressor operation.

[0127] Further, in this embodiment, the distance between the central axis of the first shaft section 311 and the central axis of the eccentric section 312 is r0 (as Figure 14 shown), the length of the projection of the medium portion 40 along the axial direction of the crankshaft 31 is L0 (as Figure 19 shown); a second sealing groove 333 is provided on a side of the orbiting scroll 33 close to the bracket 36, a sealing member 34 is provided in the second sealing groove 333, the distance between a side of the sealing member 34 close to the crankshaft 31 and the central axis of the crankshaft 31 is r3 (as Figure 21 shown), the distance between a side of the sealing member 34 away from the crankshaft 31 and the central axis of the crankshaft 31 is r4 (as Figure 21 as shown in the figure), a medium portion 40 is provided on a side of the bracket 36 adjacent to the orbiting scroll 33, and the distance between the end of the third end 403 of the medium portion 40 and the central axis of the second bearing hole 362 is R2 (as Figure 21 shown in the figure); when r0, L0, r3, r4 and R2 satisfy the relational expressions: R2 < r3 - r0 and r4 - r0 < R2 + L0 < r4 + r0, the orbiting scroll 33 performs orbital translation so that the third end 403 of the medium portion 40 is always in communication with the second pressure space 60, and the fourth end 404 of the medium portion 40 is periodically in communication with the first pressure space 50. Illustratively, the medium portion 40 in this embodiment includes an oil groove 41, a first oil hole 42 or a second oil hole 43.

[0128] Specifically, under the condition that R2 < r3 - r0 and r4 - r0 < R2 + L0 < r4 + r0, relying on the orbital motion of the orbiting scroll 33, the sealing member 34 located on the orbiting scroll 33 can move synchronously with the orbiting scroll 33, so that the first pressure space 50 and the second pressure space 60 can be periodically communicated through the medium portion 40. Thereby, there is no need to reduce the dimensions such as the depth, width of the oil groove 41 or the aperture of the oil hole, the problem that a flow groove with a smaller size is easily blocked by foreign matters is avoided, the throttling effect is effectively improved, and then the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50 can be controlled. Meanwhile, this method makes the medium portion 40 easier to process, and more convenient to adjust the pressure and the injection amount of lubricating oil, ensuring the high efficiency and reliability of the compressor operation.

[0129] Further, in this embodiment, the distance between the central axis of the first shaft section 311 and the central axis of the eccentric section 312 is r0, and the length of the projection of the medium portion 40 along the axial direction of the crankshaft 31 is L0; a second sealing groove 333 is provided on a side of the orbiting scroll 33 adjacent to the bracket 36, a sealing member 34 is provided in the second sealing groove 333, the distance between a side of the sealing member 34 adjacent to the crankshaft 31 and the central axis of the crankshaft 31 is r3, and the distance between a side of the sealing member 34 away from the crankshaft 31 and the central axis of the crankshaft 31 is r4. A medium portion 40 is provided on a side of the bracket 36 adjacent to the orbiting scroll 33, and the distance between the end of the third end 403 of the medium portion 40 and the central axis of the second bearing hole 362 is R2; when r0, L0, r3, r4 and R2 satisfy the relational expressions: r4 + r0 < R2 + L0 and r3 - r0 < R2 < r3 + r0, the orbiting scroll 33 performs orbital translation so that the third end 403 of the medium portion 40 is periodically in communication with the second pressure space 60, and the fourth end 404 of the medium portion 40 is always in communication with the first pressure space 50. Illustratively, the medium portion 40 in this embodiment includes an oil groove 41, a first oil hole 42 or a second oil hole 43.

[0130] Specifically, under the condition that r4+r0<R2+L0 and r3-r0<R2<r3+r0, relying on the orbiting motion of the orbiting scroll 33, the sealing member 34 located on the orbiting scroll 33 can move synchronously with the orbiting scroll 33, thereby enabling the first pressure space 50 and the second pressure space 60 to periodically communicate with each other through the medium portion 40. Therefore, it is not necessary to reduce the dimensions such as the depth and width of the oil groove 41 or the aperture of the oil hole, which avoids the problem that the flow groove with a smaller size is easily blocked by foreign matters, effectively improves the throttling effect, and further can control the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50. Meanwhile, this method makes the medium portion 40 easier to process, and makes the adjustment of pressure and lubricating oil injection amount more convenient, ensuring the high efficiency and reliability of compressor operation.

[0131] Further, in this embodiment, the distance between the central axis of the first shaft section 311 and the central axis of the eccentric section 312 is r0, and the length of the projection of the medium portion 40 along the axial direction of the crankshaft 31 is L0; a second sealing groove 333 is provided on a side of the orbiting scroll 33 close to the support 36, a sealing member 34 is provided in the second sealing groove 333, the distance between the side of the sealing member 34 close to the crankshaft 31 and the central axis of the crankshaft 31 is r3, and the distance between the side of the sealing member 34 away from the crankshaft 31 and the central axis of the crankshaft 31 is r4; the medium portion 40 is provided on a side of the support 36 close to the orbiting scroll 33, and the distance between the end of the third end 403 of the medium portion 40 and the central axis of the second bearing hole 362 is R2; wherein when r0, L0, r3, r4 and R2 satisfy the relational expressions: r4-r0<R2+L0<r4+r0 and r3-r0<R2<r3+r0, the orbiting scroll 33 performs orbiting translation so that the third end 403 of the medium portion 40 periodically communicates with the second pressure space 60, and the fourth end 404 of the medium portion 40 periodically communicates with the first pressure space 50. Illustratively, the medium portion 40 in this embodiment includes an oil groove 41, a first oil hole 42 or a second oil hole 43.

[0132] Specifically, under the conditions of r4-r0 < R2+L0 < r4+r0 and r3-r0 < R2 < r3+r0, relying on the rotational movement of the orbiting scroll 33, the sealing member 34 located on the orbiting scroll 33 can move synchronously with the orbiting scroll 33, so that the first pressure space 50 and the second pressure space 60 can be periodically communicated through the medium portion 40. Therefore, it is not necessary to reduce the dimensions such as the depth, width of the oil groove 41 or the aperture of the oil hole, which avoids the problem that a flow groove with smaller dimensions is easily blocked by foreign matters, effectively improves the throttling effect, and further can control the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50. Meanwhile, this method makes the medium portion 40 easier to process, and facilitates adjustment of pressure and lubricating oil injection amount, ensuring high efficiency and reliability of compressor operation.

[0133] Further, the medium portion 40 in this embodiment includes an oil groove 41, or a first oil hole 42, or a second oil hole 43. Specifically, referring to Figure 3 and Figure 7 , in an embodiment of the present application, when the medium portion 40 includes the oil groove 41, the oil groove 41 is provided on the end surface of the orbiting scroll 33 close to the bracket 36 or on the end surface of the bracket 36 close to the orbiting scroll 33, and the oil groove 41 extends along the radial direction of the crankshaft 31; or, referring to Figure 5 and Figure 9 , in another embodiment of the present application, when the medium portion 40 includes the first oil hole 42, the first oil hole 42 is provided on the side of the orbiting scroll 33 close to the bracket 36 or the side of the bracket 36 close to the orbiting scroll 33. The first oil hole 42 comprises a first hole section 421, a second hole section 422 and a third hole section 423. The first hole section 421 and the second hole section 422 both extend along the axial direction of the crankshaft 31, the first hole section 421 is located on the side of the sealing member 34 close to the crankshaft 31, and the second hole section 422 is located on the side of the sealing member 34 away from the crankshaft 31. The third hole section 423 extends along the radial direction of the crankshaft 31, and opposite ends of the third hole section 423 are respectively communicated with the first hole section 421 and the second hole section 422; or, referring to Figures 25 to 26 , in another embodiment of the present application, when the medium portion 40 includes the second oil hole 43, the second oil hole 43 is provided on the side of the orbiting scroll 33 close to the bracket 36 and extends along the axial direction of the crankshaft 31, and is disposed close to the sealing member 34; or, the second oil hole 43 is provided on the side of the bracket 36 close to the orbiting scroll 33, extends along the axial direction of the crankshaft 31, and is disposed close to the sealing member 34.

[0134] Specifically, as can be seen from the foregoing, the arrangement of the medium 40 and the sealing element 34 in this application includes at least the following two configurations: (1) A first sealing groove 363 is provided on the side of the bracket 36 near the moving scroll plate 33, and the first sealing groove 363 contains the sealing element 34; the medium 40 is provided on the side of the moving scroll plate 33 near the bracket 36; (2) A second sealing groove 333 is provided on the side of the moving scroll plate 33 near the bracket 36, and the second sealing groove 333 contains the sealing element 34; the medium 40 is provided on the side of the bracket 36 near the moving scroll plate 33. In both configurations, the medium 40 can be configured as an oil groove 41, a first oil hole 42, or a second oil hole 43, wherein the first oil hole 42 is a hole-shaped channel, and the second oil hole 43 is a blind hole. When the relationships between r0, L0, r1, r2 and R1, and between r0, L0, r3, r4 and R2 satisfy the aforementioned equations, the first pressure space 50 and the second pressure space 60 can be periodically connected through the oil groove 41, the first oil hole 42, or the second oil hole 43. This eliminates the need to reduce the depth or width of the oil groove 41, or the diameter of the first oil hole 42 or the second oil hole 43, thus avoiding the problem of small-sized flow grooves being easily blocked by foreign objects. This effectively improves the throttling effect and enables control over the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50.

[0135] Furthermore, in this embodiment, the depth H1 of the oil groove 41 along the crankshaft 31 axial direction (e.g.) Figure 19 As shown, the relationship must be satisfied: H1 ≥ 0.05 mm. For example, H1 can be set to 0.05 mm, 0.06 mm, 0.08 mm, 0.1 mm, 0.12 mm, 0.14 mm, 0.16 mm, etc. Specifically, in this embodiment, the depth and width of the oil groove 41 determine the flow area, thereby controlling the flow rate when the first pressure space 50 and the second pressure space 60 are connected. When H1 is less than 0.05 mm, the depth of the oil groove 41 is too shallow, resulting in high processing precision requirements, making it difficult to process the oil groove 41, and the oil groove 41 is easily blocked by impurities, thus adversely affecting the reliability of the compressor operation.

[0136] Furthermore, in this embodiment, the minimum diameter D5 of the first oil hole 42 satisfies the relationship: D5 ≥ 0.1 mm. For example, D5 can be set to 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1 mm, etc. Specifically, since the first oil hole 42 in this embodiment includes a first hole segment 421, a second hole segment 422, and a third hole segment 423, the minimum diameter of the first oil hole 42 refers to the hole segment with the smallest diameter among the first hole segment 421, the second hole segment 422, and the third hole segment 423 satisfying the above relationship. The diameter of the first oil hole 42 determines the flow area, thereby controlling the flow rate of lubricating oil when the first pressure space 50 and the second pressure space 60 are connected. When D5 is less than 0.1mm, the diameter of the first oil hole 42 is too small, resulting in high machining accuracy requirements. It is not easy to machine the first oil hole 42, and the first oil hole 42 is easily blocked by impurities, which has an adverse effect on the reliability of the compressor operation.

[0137] Furthermore, in this embodiment, the depth H2 of the second oil hole 43 along the crankshaft 31 satisfies the relationship: H2 ≥ 0.05 mm. For example, H2 can be set to 0.05 mm, 0.06 mm, 0.08 mm, 0.1 mm, 0.12 mm, 0.14 mm, 0.16 mm, etc. Specifically, the depth and width of the second oil hole 43 determine the flow area, thereby controlling the flow rate of lubricating oil when the first pressure space 50 and the second pressure space 60 are connected. When H2 is less than 0.05 mm, the depth of the second oil hole 43 is too shallow, resulting in high machining accuracy requirements, making it difficult to machine the second oil hole 43, and the second oil hole 43 is easily blocked by impurities, thus adversely affecting the reliability of the compressor operation.

[0138] Further, see Figures 10 to 11 As shown, the medium part 40 in this embodiment includes a third oil hole 44, which is disposed on the stationary scroll plate 32 or the moving scroll plate 33. The third oil hole 44 includes a fourth hole segment 441, a fifth hole segment 442 and a sixth hole segment 443. The fourth hole segment 441 and the fifth hole segment 442 both extend along the axial direction of the crankshaft 31, and the sixth hole segment 443 extends along the radial direction of the crankshaft 31. The two opposite ends of the sixth hole segment 443 are respectively connected to the fourth hole segment 441 and the fifth hole segment 442.

[0139] Specifically, in this embodiment, the medium 40 can also be configured as a third oil hole 44, which is a hole-shaped channel. The fourth hole segment 441 and the fifth hole segment 442 in the third oil hole 44 are arranged at a distance along the radial direction of the crankshaft 31 and extend along the radial direction of the crankshaft 31. The two ends of the sixth hole segment 443 are respectively connected to the fourth hole segment 441 and the fifth hole segment 442. In this way, lubricating oil can enter from the fourth hole segment 441, flow through the sixth hole segment 443 to the fifth hole segment 442, and then flow out from the fifth hole segment 442.

[0140] Further, see Figure 10 As shown, in this embodiment, the stationary scroll 32 is provided with a third oil hole 44. The fourth hole segment 441 and the fifth hole segment 442 both extend along the axial direction of the crankshaft 31 and extend in the same direction. The fourth hole segment 441 is closer to the crankshaft 31 than the fifth hole segment 442. The opening of the fourth hole segment 441 is connected to the second pressure space 60. The opening of the fifth hole segment 442 is located at the sealing surface between the moving scroll 33 and the stationary scroll 32. When the moving scroll 33 rotates and translates, the opening of the fourth hole segment 441 is always connected to the second pressure space 60, and the opening of the fifth hole segment 442 is periodically connected to the first pressure space 50.

[0141] Specifically, in this embodiment, the third oil hole 44 is located on the stationary scroll plate 32, and the opening of the fifth hole section 442 is located at the sealing surface between the moving scroll plate 33 and the stationary scroll plate 32. During the rotation and translation of the moving scroll plate 33, the opening of the fourth hole section 441 is always connected to the second pressure space 60, while the opening of the fifth hole section 442 is periodically connected to the first pressure space 50. In this way, the first pressure space 50 and the second pressure space 60 can be periodically connected through the medium section 40, thus eliminating the need to reduce the diameter of the third oil hole 44 and avoiding the problem of the smaller-sized third oil hole 44 being easily blocked by foreign objects. This effectively improves the throttling effect, thereby controlling the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50. At the same time, this method makes the medium section 40 easier to process, and makes it more convenient to adjust the pressure and the amount of lubricating oil injected, ensuring the high efficiency and reliability of the compressor operation.

[0142] Further, see Figure 10As shown, the stationary scroll plate 32 in this embodiment is provided with a third oil hole 44. The fourth hole segment 441 and the fifth hole segment 442 both extend along the axial direction of the crankshaft 31 and extend in the same direction. The fourth hole segment 441 is closer to the crankshaft 31 than the fifth hole segment 442. The opening of the fourth hole segment 441 is located close to the second pressure space 60. The opening of the fifth hole segment 442 is connected to the first pressure space 50. When the moving scroll plate 33 rotates and translates, the opening of the fourth hole segment 441 is periodically connected to the second pressure space 60, and the opening of the fifth hole segment 442 is always connected to the first pressure space 50.

[0143] Specifically, in this embodiment, the third oil hole 44 is located on the stationary scroll plate 32, and the opening of the fourth hole section 441 is located close to the second pressure space 60. During the rotation and translation of the moving scroll plate 33, the opening of the fourth hole section 441 is periodically connected to the second pressure space 60, and the opening of the fifth hole section 442 is always connected to the first pressure space 50. In this way, the first pressure space 50 and the second pressure space 60 can be periodically connected through the medium section 40, so there is no need to reduce the size of the third oil hole 44, avoiding the problem that small-sized oil holes are easily blocked by foreign objects, effectively improving the throttling effect, thereby controlling the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50. At the same time, this method makes the medium section 40 easier to process, and makes it more convenient to adjust the pressure and the amount of lubricating oil injected, ensuring the high efficiency and reliability of the compressor operation.

[0144] Further, see Figure 10 As shown, in this embodiment, the stationary scroll 32 is provided with a third oil hole 44. The fourth hole segment 441 and the fifth hole segment 442 both extend along the axial direction of the crankshaft 31 and extend in the same direction. The fourth hole segment 441 is closer to the crankshaft 31 than the fifth hole segment 442. The opening of the fourth hole segment 441 is located close to the second pressure space 60. The opening of the fifth hole segment 442 is located at the sealing surface between the moving scroll 33 and the stationary scroll 32. When the moving scroll 33 rotates and translates, the opening of the fourth hole segment 441 periodically communicates with the second pressure space 60, and the opening of the fifth hole segment 442 periodically communicates with the first pressure space 50.

[0145] Specifically, in this embodiment, the third oil hole 44 is located on the stationary scroll plate 32, and the opening of the fourth hole section 441 is located close to the second pressure space 60, while the opening of the fifth hole section 442 is located at the sealing surface between the moving scroll plate 33 and the stationary scroll plate 32. During the rotation and translation of the moving scroll plate 33, the opening of the fourth hole section 441 periodically communicates with the second pressure space 60, and the opening of the fifth hole section 442 periodically communicates with the first pressure space 50. In this way, the first pressure space 50 and the second pressure space 60 can be periodically connected through the medium section 40, thus eliminating the need to reduce the diameter of the third oil hole 44 and avoiding the problem of small-sized oil holes being easily blocked by foreign objects. This effectively improves the throttling effect, thereby controlling the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50. At the same time, this method makes the medium section 40 easier to process, and makes it more convenient to adjust the pressure and the amount of lubricating oil injected, ensuring the high efficiency and reliability of the compressor operation.

[0146] Further, see Figure 11 As shown, in this embodiment, the moving scroll 33 is provided with a third oil hole 44. The fourth hole segment 441 and the fifth hole segment 442 both extend along the axial direction of the crankshaft 31 and extend in opposite directions. The fourth hole segment 441 is closer to the crankshaft 31 than the fifth hole segment 442. The opening of the fourth hole segment 441 is connected to the second pressure space 60. The opening of the fifth hole segment 442 is located at the sealing surface between the moving scroll 33 and the stationary scroll 32. When the moving scroll 33 rotates and translates, the fourth hole segment 441 is always connected to the second pressure space 60, and the opening of the fifth hole segment 442 is periodically connected to the first pressure space 50.

[0147] Specifically, in this embodiment, the third oil hole 44 is located on the moving scroll plate 33, and the opening of the fourth hole section 441 is connected to the second pressure space 60, while the opening of the fifth hole section 442 is located at the sealing surface of the moving scroll plate 33 and the stationary scroll plate 32. When the moving scroll plate 33 rotates and moves horizontally, the third oil hole 44 will move synchronously with the moving scroll plate 33. This allows the first pressure space 50 and the second pressure space 60 to be periodically connected through the medium section 40, effectively improving the throttling effect. This enables control over the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50. At the same time, this method makes the medium section 40 easier to process, and makes it more convenient to adjust the pressure and the amount of lubricating oil injected, ensuring the high efficiency and reliability of the compressor operation.

[0148] Further, see Figure 11As shown, in this embodiment, the moving scroll 33 is provided with a third oil hole 44. The fourth hole segment 441 and the fifth hole segment 442 both extend along the axial direction of the crankshaft 31 and extend in opposite directions. The fourth hole segment 441 is closer to the crankshaft 31 than the fifth hole segment 442. The opening of the fourth hole segment 441 is located close to the second pressure space 60. The opening of the fifth hole segment 442 is located at the sealing surface between the moving scroll 33 and the stationary scroll 32. When the moving scroll 33 rotates and translates, the fourth hole segment 441 periodically communicates with the second pressure space 60, and the opening of the fifth hole segment 442 periodically communicates with the first pressure space 50.

[0149] Specifically, in this embodiment, the third oil hole 44 is located on the moving scroll plate 33, and the opening of the fourth hole section 441 is located close to the second pressure space 60, while the opening of the fifth hole section 442 is located at the sealing surface of the moving scroll plate 33 and the stationary scroll plate 32. When the moving scroll plate 33 rotates and moves horizontally, the third oil hole 44 will move synchronously with the moving scroll plate 33. This allows the first pressure space 50 and the second pressure space 60 to be periodically connected through the medium section 40, effectively improving the throttling effect. This enables control over the pressure value of the first pressure space 50 and the flow rate of lubricating oil delivered from the second pressure space 60 to the first pressure space 50. At the same time, this method makes the medium section 40 easier to process and makes it more convenient to adjust the pressure and the amount of lubricating oil injected, ensuring the high efficiency and reliability of the compressor operation.

[0150] Furthermore, in this embodiment, the minimum diameter D6 of the third oil hole 44 satisfies the relationship: D6 ≥ 0.1 mm. For example, D6 can be set to 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1 mm, etc. Specifically, since the third oil hole 44 in this embodiment includes a fourth segment 441, a fifth segment 442, and a sixth segment 443, the minimum diameter of the third oil hole 44 refers to the segment with the smallest diameter among the fourth segment 441, the fifth segment 442, and the sixth segment 443 satisfying the above relationship. The diameter of the third oil hole 44 determines the flow area, thereby enabling control of the flow rate of lubricating oil when the first pressure space 50 and the second pressure space 60 are connected. When D6 is less than 0.1mm, the diameter of the third oil hole 44 is too small, resulting in high machining accuracy requirements. It is not easy to machine the third oil hole 44, and the third oil hole 44 is easily blocked by impurities, which has an adverse effect on the reliability of the compressor operation.

[0151] Furthermore, the median 40 in this embodiment includes at least one. When the median 40 includes multiple median 40s, the multiple median 40s are arranged circumferentially on the stationary scroll plate 32, the moving scroll plate 33, or the bracket 36 along the crankshaft 31. The multiple median 40s include at least one of the following: oil groove 41, first oil hole 42, second oil hole 43, and third oil hole 44.

[0152] Specifically, the purpose of the medium section 40 is to form a flow channel to connect the first pressure space 50 and the second pressure space 60, thereby transporting lubricating oil from the second pressure space 60 to the first pressure space 50. When a single medium section 40 cannot meet the oil supply demand, or to improve the uniformity of oil supply from the medium section 40 to the first pressure space 50, multiple or various types of medium sections 40 can be provided to meet the requirements of high efficiency and reliability of compressor operation. It is worth noting that when multiple medium sections 40 are provided on the stationary scroll plate 32, the moving scroll plate 33, or the support 36, the medium section 40 may include only the oil groove 41, the first oil hole 42, the second oil hole 43, or the third oil hole 44, or it may include at least two of the oil groove 41, the first oil hole 42, the second oil hole 43, and the third oil hole 44. For example, the stationary scroll plate 32, the moving scroll plate 33, or the support 36 may simultaneously provide the oil groove 41, the first oil hole 42, the second oil hole 43, and the third oil hole 44.

[0153] Combination Figures 22 to 31 As shown, the first pressure space 50 and the second pressure space 60 in this application have the following connectivity:

[0154] (1) Figure 22 Specifically, it shows the case where the oil trough 41 is located on the side of the moving scroll plate 33 near the support 36, and the seal 34 is located on the side of the support 36 near the moving scroll plate 33.

[0155] (2) Figure 23 This illustration shows the configuration where the oil trough 41 is located on the side of the moving scroll plate 33 near the support 36, and the seal 34 is located on the side of the support 36 near the moving scroll plate 33. Specifically, when the oil trough 41 is located... Figure 23 When the position shown is such that the first end 401 of the oil tank 41 is always connected to the second pressure space 60, and the second end 402 of the oil tank 41 is periodically connected to the first pressure space 50;

[0156] (3) Figure 24 This illustration shows the configuration where the oil trough 41 is located on the side of the moving scroll plate 33 near the support 36, and the seal 34 is located on the side of the support 36 near the moving scroll plate 33. Specifically, when the oil trough 41 is located... Figure 24 When the position shown is such that the first end 401 of the oil tank 41 is periodically connected to the second pressure space 60, and the second end 402 of the oil tank 41 is always connected to the first pressure space 50;

[0157] (4) Figure 25 as well as Figure 26 This illustrates a configuration where the second oil hole 43 is located on the side of the moving scroll plate 33 near the support 36, and the seal 34 is located on the side of the support 36 near the moving scroll plate 33. Specifically, when the second oil hole 43 is located... Figure 25 as well as Figure 26 At the position shown, the second oil hole 43 makes the second pressure space 60 and the first pressure space 50 periodically connected;

[0158] (5) Figure 27 Specifically, it shows the case where the oil trough 41 is located on the side of the bracket 36 near the moving scroll plate 33 and the seal 34 is located on the side of the moving scroll plate 33 near the bracket 36.

[0159] (6) Figure 28 This illustration shows the configuration where the oil trough 41 is positioned on the side of the bracket 36 near the moving scroll plate 33, and the seal 34 is positioned on the side of the moving scroll plate 33 near the bracket 36. Specifically, when the oil trough 41 is located... Figure 28 When the position shown is such that the third end 403 of the oil tank 41 is always connected to the second pressure space 60, and the fourth end 404 of the oil tank 41 is periodically connected to the first pressure space 50;

[0160] (7) Figure 29 This illustration shows the configuration where the oil trough 41 is positioned on the side of the bracket 36 near the moving scroll plate 33, and the seal 34 is positioned on the side of the moving scroll plate 33 near the bracket 36. Specifically, when the oil trough 41 is located... Figure 29 When the position shown is such that the third end 403 of the oil tank 41 is periodically connected to the second pressure space 60, and the fourth end 404 of the oil tank 41 is always connected to the first pressure space 50;

[0161] (8) Figure 30 as well as Figure 31 This illustration shows a configuration where the first oil hole 42 is located on the side of the bracket 36 near the moving scroll plate 33, and the seal 34 is located on the side of the moving scroll plate 33 near the bracket 36. Specifically, when the first oil hole 42 is located... Figure 30 as well as Figure 31 When the position shown is such that the third end 403 of the first oil hole 42 is periodically connected to the second pressure space 60, and the fourth end 404 of the first oil hole 42 is periodically connected to the first pressure space 50.

[0162] As can be seen from the above embodiments, this application provides a medium 40 on the stationary scroll plate 32, the moving scroll plate 33, or the bracket 36. The medium 40 has an on / off function, which can periodically connect the first pressure space 50 and the second pressure space 60, thereby controlling the amount of oil supplied from the second pressure space 60 to the first pressure space 50, effectively preventing insufficient oil supply to the compressor, ensuring the performance and reliability of the compressor, and extending the service life of the compressor.

[0163] 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.

[0164] 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.

[0165] 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.

[0166] 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 Q of the air conditioning system satisfies the relationship: 2500W ≤ Q ≤ 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 positioned closer to the bottom of the receiving cavity (101) than the motor (20). The pump body assembly (30) includes a crankshaft (31), a stationary scroll plate (32), a moving scroll plate (33), a seal (34), an anti-rotation component (35), and a bracket (36). The crankshaft (31) is rotatably disposed within the receiving cavity (101) and passes through the motor (20). The stationary scroll plate (32), the moving scroll plate (33), the sealing element (34), the anti-rotation element (35), and the bracket (36) are provided. 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. 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). The motor (20) is sleeved on the first shaft segment (311). The stationary scroll plate (32) has a first bearing portion on the side away from the moving scroll plate (33). (322), the first bearing part (322) has a first bearing hole (323), the moving scroll disk (33) has an eccentric bearing hole (332) through which the eccentric section (312) passes, the bracket (36) is provided with a second bearing part (361) on the side away from the moving scroll disk (33), the second bearing part (361) has a second bearing hole (362), the stationary scroll disk (32) is sleeved on the first shaft section (311) or the second shaft section (313) through the first bearing hole (323), and the bracket (36) is sleeved on the second shaft section (313) or the first shaft section (311) through the second bearing hole (362); The crankshaft (31) is provided with an oil supply channel (314). The seal (34) and the anti-rotation component (35) are both disposed between the moving scroll plate (33) and the bracket (36). The anti-rotation component (35) is disposed on the side of the seal (34) away from the crankshaft (31). The side of the seal (34) away from the crankshaft (31), together with the stationary scroll plate (32), the moving scroll plate (33), and the bracket (36), forms a first pressure space (5). 0), the seal (34) is arranged with the moving scroll (33) and the bracket (36) on the side near the crankshaft (31) to form a second pressure space (60). A medium (40) is provided on one of the three: the stationary scroll (32), the moving scroll (33) and the bracket (36). When the moving scroll (33) rotates and moves, the medium (40) periodically delivers the lubricating oil from the second pressure space (60) to the first pressure space (50).

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: 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.

3. 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 (3111) that mates with the first bearing hole (323) or the second bearing hole (362). Along the axial direction of the crankshaft (31), the width W1 of the first support fitting portion (3111) satisfies the relationship: 22mm ≤ W1 ≤ 35mm; and / or, The first shaft segment (311) has a first support fitting part (3111) that mates with the first bearing hole (323) or the second bearing hole (362). Along the axial direction of the crankshaft (31), the maximum distance L1 between the end of the first support fitting part (3111) 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.

4. The compressor for use in an air conditioning system according to claim 1, characterized in that, The diameter D4 of the oil supply channel (314) satisfies the following relationship: D4≤6mm.

5. The compressor for use in an air conditioning system according to claim 1, characterized in that, The minimum operating frequency F1 of the compressor satisfies the following relationship: F1≤15Hz.

6. The compressor for use in an air conditioning system according to claim 1, characterized in that, The amount of lubricating oil V injected into the compressor satisfies the following relationship: 200mL≤V≤350mL.

7. The compressor for use in an air conditioning system according to claim 1, characterized in that, A first sealing groove (363) is provided on a side of the bracket (36) close to the orbiting scroll (33), the first sealing groove (363) is circumferentially arranged around the second bearing hole (362), the sealing member (34) is arranged in the first sealing groove (363), the medium portion (40) is provided on a side of the orbiting scroll (33) close to the bracket (36), the medium portion (40) has a first end (401) close to the eccentric bearing hole (332) and a second end (402) far from the eccentric bearing hole (332), the first end (401) extends to the eccentric bearing hole (332) or is spaced apart from the eccentric bearing hole (332) by a predetermined distance; or, A second sealing groove (333) is provided on a side of the orbiting scroll (33) close to the bracket (36), the second sealing groove (333) is circumferentially arranged around the eccentric bearing hole (332), the sealing member (34) is arranged in the second sealing groove (333), the medium portion (40) is provided on a side of the bracket (36) close to the orbiting scroll (33), the medium portion (40) has a third end (403) close to the second bearing hole (362) and a fourth end (404) far from the second bearing hole (362), the third end (403) extends to the second bearing hole (362) or is spaced apart from the second bearing hole (362) by a predetermined distance.

8. The compressor for use in an air conditioning system according to claim 7, characterized in that, A distance between a central axis of the first shaft section (311) and a central axis of the eccentric section (312) is r0, and a projection length of the medium portion (40) along an axial direction of the crankshaft (31) is L0; A first sealing groove (363) is provided on a side of the bracket (36) close to the orbiting scroll (33), the sealing member (34) is arranged in the first sealing groove (363), a distance between a side of the sealing member (34) close to the crankshaft (31) and a central axis of the crankshaft (31) is r1, a distance between a side of the sealing member (34) far from the crankshaft (31) and the central axis of the crankshaft (31) is r2, the medium portion (40) is provided on a side of the orbiting scroll (33) close to the bracket (36), a distance between an end of the first end (401) of the medium portion (40) and a central axis of the eccentric bearing hole (332) is R1; wherein, when r0, L0, r1, r2 and R1 satisfy the relational expression: R1+r0<r1 and R1+L0-r0<r2<R1+L0+r0, the orbiting scroll (33) performs orbital translation such that the first end (401) of the medium portion (40) is always in communication with the second pressure space (60), and the second end (402) of the medium portion (40) is periodically in communication with the first pressure space (50).

9. The compressor for use in an air conditioning system according to claim 7, characterized in that, The distance between the central axis of the first shaft section (311) and the central axis of the eccentric section (312) is r0, and the length of the projection of the medium portion (40) along the axial direction of the crankshaft (31) is L0; A first sealing groove (363) is provided on a side of the support (36) adjacent to the orbiting scroll (33), the sealing member (34) is disposed in the first sealing groove (363), the distance between a side of the sealing member (34) adjacent to the crankshaft (31) and the central axis of the crankshaft (31) is r1, the distance between a side of the sealing member (34) away from the crankshaft (31) and the central axis of the crankshaft (31) is r2, the medium portion (40) is provided on a side of the orbiting scroll (33) adjacent to the support (36), and the distance between an end of the first end (401) of the medium portion (40) and the central axis of the eccentric bearing hole (332) is R1; wherein when r0, L0, r1, r2 and R1 satisfy the relational expressions: r2<R1+L0-r0 and R1-r0<r1<R1+r0, the orbiting scroll (33) performs orbital translation so that the first end (401) of the medium portion (40) periodically communicates with the second pressure space (60), and the second end (402) of the medium portion (40) always communicates with the first pressure space (50).

10. The compressor for use in an air conditioning system according to claim 7, characterized in that, The distance between the central axis of the first shaft section (311) and the central axis of the eccentric section (312) is r0, and the length of the projection of the medium portion (40) along the axial direction of the crankshaft (31) is L0; A first sealing groove (363) is provided on a side of the support (36) adjacent to the orbiting scroll (33), the sealing member (34) is disposed in the first sealing groove (363), the distance between a side of the sealing member (34) adjacent to the crankshaft (31) and the central axis of the crankshaft (31) is r1, the distance between a side of the sealing member (34) away from the crankshaft (31) and the central axis of the crankshaft (31) is r2, the medium portion (40) is provided on a side of the orbiting scroll (33) adjacent to the support (36), and the distance between an end of the first end (401) of the medium portion (40) and the central axis of the eccentric bearing hole (332) is R1; wherein when r0, L0, r1, r2 and R1 satisfy the relational expressions: R1+L0-r0<r2<R1+L0+r0 and R1-r0<r1<R1+r0, the orbiting scroll (33) performs orbital translation so that the first end (401) of the medium portion (40) periodically communicates with the second pressure space (60), and the second end (402) of the medium portion (40) periodically communicates with the first pressure space (50).

11. The compressor for use in an air conditioning system according to claim 7, characterized in that, The distance between the central axis of the first shaft section (311) and the central axis of the eccentric section (312) is r0, and the length of the projection of the medium portion (40) along the axial direction of the crankshaft (31) is L0; A second sealing groove (333) is provided on a side of said orbiting scroll (33) close to said bracket (36), said sealing member (34) is arranged in said second sealing groove (333), a distance between a side of said sealing member (34) close to said crankshaft (31) and a central axis of said crankshaft (31) is r3, a distance between a side of said sealing member (34) away from said crankshaft (31) and the central axis of said crankshaft (31) is r4, said medium portion (40) is provided on a side of said bracket (36) close to said orbiting scroll (33), a distance between an end of a third end (403) of said medium portion (40) and a central axis of a second bearing hole (362) is R2; wherein, when r0, L0, r3, r4 and R2 satisfy the relational expressions: R2 < r3 - r0 and r4 - r0 < R2 + L0 < r4 + r0, said orbiting scroll (33) performs orbiting translational motion such that the third end (403) of said medium portion (40) is always in communication with said second pressure space (60), and a fourth end (404) of said medium portion (40) is periodically in communication with said first pressure space (50).

12. The compressor for use in an air conditioning system according to claim 7, characterized in that, a distance between a central axis of said first shaft section (311) and a central axis of said eccentric section (312) is r0, and a length of a projection of said medium portion (40) along an axial direction of said crankshaft (31) is L0; A second sealing groove (333) is provided on a side of said orbiting scroll (33) close to said bracket (36), said sealing member (34) is arranged in said second sealing groove (333), a distance between a side of said sealing member (34) close to said crankshaft (31) and a central axis of said crankshaft (31) is r3, a distance between a side of said sealing member (34) away from said crankshaft (31) and the central axis of said crankshaft (31) is r4, said medium portion (40) is provided on a side of said bracket (36) close to said orbiting scroll (33), a distance between an end of a third end (403) of said medium portion (40) and a central axis of a second bearing hole (362) is R2; wherein, when r0, L0, r3, r4 and R2 satisfy the relational expressions: r4 + r0 < R2 + L0 and r3 - r0 < R2 < r3 + r0, said orbiting scroll (33) performs orbiting translational motion such that the third end (403) of said medium portion (40) is periodically in communication with said second pressure space (60), and a fourth end (404) of said medium portion (40) is always in communication with said first pressure space (50).

13. The compressor for use in an air conditioning system according to claim 7, characterized in that, a distance between a central axis of said first shaft section (311) and a central axis of said eccentric section (312) is r0, and a length of a projection of said medium portion (40) along an axial direction of said crankshaft (31) is L0; A second sealing groove (333) is provided on a side of said orbiting scroll (33) adjacent to said support (36), said sealing member (34) is disposed in said second sealing groove (333), the distance between a side of said sealing member (34) adjacent to said crankshaft (31) and the central axis of said crankshaft (31) is r3, the distance between a side of said sealing member (34) away from said crankshaft (31) and the central axis of said crankshaft (31) is r4, said medium portion (40) is provided on a side of said support (36) adjacent to said orbiting scroll (33), the distance between an end of a third end (403) of said medium portion (40) and the central axis of a second bearing hole (362) is R2; wherein, when r0, L0, r3, r4 and R2 satisfy the relational expressions: r4-r0<R2+L0<r4+r0, and r3-r0<R2<r3+r0, said orbiting scroll (33) performs orbiting translational motion so that the third end (403) of said medium portion (40) periodically communicates with a second pressure space (60), and a fourth end (404) of said medium portion (40) periodically communicates with a first pressure space (50).

14. The compressor for use in an air conditioning system according to any one of claims 1 to 13, characterized in that, said medium portion (40) comprises an oil groove (41), or a first oil hole (42), or a second oil hole (43); when said medium portion (40) comprises said oil groove (41), said oil groove (41) is provided on an end face of said orbiting scroll (33) adjacent to said support (36) or on an end face of said support (36) adjacent to said orbiting scroll (33), and said oil groove (41) extends in a radial direction of said crankshaft (31); or, when said medium portion (40) comprises said first oil hole (42), said first oil hole (42) is provided on a side of said orbiting scroll (33) adjacent to said support (36) or on a side of said support (36) adjacent to said orbiting scroll (33), said first oil hole (42) comprises a first hole section (421), a second hole section (422) and a third hole section (423), both said first hole section (421) and said second hole section (422) extend in an axial direction of said crankshaft (31), said first hole section (421) is located on a side of said sealing member (34) adjacent to said crankshaft (31), said second hole section (422) is located on a side of said sealing member (34) away from said crankshaft (31), said third hole section (423) extends in a radial direction of said crankshaft (31), and opposite ends of said third hole section (423) are respectively in communication with said first hole section (421) and said second hole section (422); or, When the medium (40) includes a second oil hole (43), the second oil hole (43) is disposed on the side of the moving scroll plate (33) near the support (36) and extends axially along the crankshaft (31), and the second oil hole (43) is disposed near the seal (34), or the second oil hole (43) is disposed on the side of the support (36) near the moving scroll plate (33) and extends axially along the crankshaft (31), and the second oil hole (43) is disposed near the seal (34).

15. The compressor for use in an air conditioning system according to claim 14, characterized in that, The depth H1 of the oil groove (41) along the axial direction of the crankshaft (31) satisfies the following relationship: H1 ≥ 0.05 mm; and / or, The minimum diameter D5 of the first oil hole (42) satisfies the following relationship: D5 ≥ 0.1 mm; and / or, The depth H2 of the second oil hole (43) along the axial direction of the crankshaft (31) satisfies the following relationship: H2≥0.05mm.

16. The compressor for use in an air conditioning system according to claim 1, characterized in that, The medium (40) includes a third oil hole (44), which is disposed on the stationary scroll plate (32) or the moving scroll plate (33). The third oil hole (44) includes a fourth hole segment (441), a fifth hole segment (442) and a sixth hole segment (443). The fourth hole segment (441) and the fifth hole segment (442) both extend along the axial direction of the crankshaft (31). The sixth hole segment (443) extends radially along the crankshaft (31) and its two opposite ends are connected to the fourth hole segment (441) and the fifth hole segment (442) respectively.

17. The compressor for use in an air conditioning system according to claim 16, characterized in that, The stationary scroll plate (32) is provided with the third oil hole (44). The fourth hole segment (441) and the fifth hole segment (442) both extend along the axial direction of the crankshaft (31) and extend in the same direction. The fourth hole segment (441) is closer to the crankshaft (31) than the fifth hole segment (442). The opening of the fourth hole segment (441) is connected to the second pressure space (60). The opening of the fifth hole segment (442) is located at the sealing surface between the moving scroll plate (33) and the stationary scroll plate (32). When the moving scroll plate (33) rotates and translates, the opening of the fourth hole segment (441) is always connected to the second pressure space (60), and the opening of the fifth hole segment (442) is periodically connected to the first pressure space (50).

18. The compressor for use in an air conditioning system according to claim 16, characterized in that, The stationary scroll plate (32) is provided with the third oil hole (44), wherein the fourth hole segment (441) and the fifth hole segment (442) both extend along the axial direction of the crankshaft (31) and extend in the same direction. The fourth hole segment (441) is closer to the crankshaft (31) than the fifth hole segment (442). The opening of the fourth hole segment (441) is located close to the second pressure space (60), and the opening of the fifth hole segment (442) is connected to the first pressure space (50). When the moving scroll plate (33) rotates and translates, the opening of the fourth hole segment (441) is periodically connected to the second pressure space (60), and the opening of the fifth hole segment (442) is always connected to the first pressure space (50).

19. The compressor for use in an air conditioning system according to claim 16, characterized in that, The stationary scroll plate (32) is provided with the third oil hole (44). The fourth hole segment (441) and the fifth hole segment (442) both extend along the axial direction of the crankshaft (31) and extend in the same direction. The fourth hole segment (441) is closer to the crankshaft (31) than the fifth hole segment (442). The opening of the fourth hole segment (441) is located close to the second pressure space (60). The opening of the fifth hole segment (442) is located at the sealing surface between the moving scroll plate (33) and the stationary scroll plate (32). When the moving scroll plate (33) rotates and translates, the opening of the fourth hole segment (441) periodically communicates with the second pressure space (60), and the opening of the fifth hole segment (442) periodically communicates with the first pressure space (50).

20. The compressor for use in an air conditioning system according to claim 16, characterized in that, The moving scroll plate (33) is provided with the third oil hole (44), wherein the fourth hole segment (441) and the fifth hole segment (442) both extend along the axial direction of the crankshaft (31) and extend in opposite directions. The fourth hole segment (441) is closer to the crankshaft (31) than the fifth hole segment (442). The opening of the fourth hole segment (441) is connected to the second pressure space (60). The opening of the fifth hole segment (442) is located at the sealing surface of the moving scroll plate (33) and the stationary scroll plate (32). When the moving scroll plate (33) rotates and translates, the fourth hole segment (441) is always connected to the second pressure space (60), and the opening of the fifth hole segment (442) is periodically connected to the first pressure space (50).

21. The compressor for use in an air conditioning system according to claim 16, characterized in that, The moving scroll plate (33) is provided with the third oil hole (44), wherein the fourth hole segment (441) and the fifth hole segment (442) both extend along the axial direction of the crankshaft (31) and extend in opposite directions. The fourth hole segment (441) is closer to the crankshaft (31) than the fifth hole segment (442). The opening of the fourth hole segment (441) is located close to the second pressure space (60). The opening of the fifth hole segment (442) is located at the sealing surface of the moving scroll plate (33) and the stationary scroll plate (32). When the moving scroll plate (33) rotates and translates, the fourth hole segment (441) periodically communicates with the second pressure space (60), and the opening of the fifth hole segment (442) periodically communicates with the first pressure space (50).

22. The compressor for use in an air conditioning system according to any one of claims 16 to 21, characterized in that, The minimum diameter D6 of the third oil hole (44) satisfies the following relationship: D6≥0.1mm.

23. The compressor for use in an air conditioning system according to claim 1, characterized in that, The mediating section (40) includes at least one. When the mediating section (40) includes multiple mediating sections (40), the multiple mediating sections (40) are arranged circumferentially on the stationary scroll plate (32), the moving scroll plate (33), or the bracket (36) along the crankshaft (31), and the multiple mediating sections (40) include at least one of an oil groove (41), a first oil hole (42), a second oil hole (43), and a third oil hole (44).

24. 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 23.

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