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 support. The sealing element is arranged between the dynamic scroll disc and the support. The sealing element, the dynamic scroll disc and the support surround to form a first back pressure space. The sealing element, the dynamic scroll disc, the static scroll disc and the support surround to form a second back pressure space. The pump body assembly has a first channel and a second channel. The first channel is communicated with the first back pressure space and the second back pressure space. The second channel is communicated with a compression cavity and the second back pressure space. In the projection along the axial direction of the crankshaft, the ratio of the projection area S1 of the first back pressure space to the projection area S2 of the dynamic scroll disc satisfies the relationship formula: 0.089<=S1 / S2<=0.298. The application can solve the problem that the pressure of the back pressure environment in the scroll compressor in the prior art has a bad influence on the energy efficiency and reliability of the scroll compressor.

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. While air conditioner manufacturers could improve energy efficiency by using larger evaporators and condensers, this approach often fails due to the drastically increased cost and low cost-effectiveness. The compressor is the core component of an air conditioner, and its energy efficiency significantly impacts the overall energy efficiency of the air conditioner. Therefore, air conditioner manufacturers are placing increasingly higher demands on the energy efficiency of compressors.

[0003] In scroll compressors, where the internal environment is high-pressure, a back pressure environment is required on the back of the moving plate (the side opposite to the scroll) to ensure the moving plate remains in close contact with the stationary plate. The average pressure of this back pressure environment must be greater than the compressor's suction pressure and less than its discharge pressure. However, the pressure of the back pressure environment in existing scroll compressors is difficult to regulate; excessively high or low pressure will negatively impact the compressor's 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, in order to solve the problem that the pressure of the back pressure environment in the existing scroll compressor has an adverse effect on the energy efficiency and reliability of the scroll compressor.

[0005] According to one aspect of this application, a compressor for use in an air conditioning system is provided, the compressor comprising a vertical variable frequency scroll compressor, the compressor further comprising:

[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 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 meshing of the first scroll tooth and the second scroll tooth forms a compression cavity.

[0009] The housing is provided with an intake pipe and an exhaust pipe. The intake pipe is connected to the pump body assembly, and the exhaust pipe is connected to the accommodating cavity. The crankshaft includes a first shaft section, an eccentric section, and a second shaft section arranged sequentially along its own axis. A first bearing portion is provided on the side of the stationary scroll disk away from the moving scroll disk. The first bearing portion has a first bearing hole. A second bearing portion is provided on the side of the bracket away from the moving scroll disk. The second bearing portion has a second bearing hole. The moving scroll disk has an eccentric bearing hole. The motor is sleeved on the first shaft section through the rotor. The stationary scroll disk is sleeved on the first shaft section or the second shaft section through the first bearing hole. The moving scroll disk is sleeved on the eccentric section through the eccentric bearing hole. The bracket is sleeved on the second shaft section or the first shaft section through the second bearing hole. The anti-rotation component is provided between the moving scroll disk and the bracket.

[0010] The sealing element is disposed between the moving scroll plate and the bracket. The side of the sealing element closer to the crankshaft forms a first back pressure space between the moving scroll plate and the bracket. The side of the sealing element away from the crankshaft forms a second back pressure space between the moving scroll plate, the stationary scroll plate and the bracket. Both the first back pressure space and the second back pressure space are arranged around the crankshaft circumferentially.

[0011] The pump body assembly has a first channel and a second channel, the first channel being connected to the first back pressure space and the second back pressure space, the second channel being connected to the compression chamber and the second back pressure space, and the first back pressure space being connected to the receiving chamber;

[0012] Within the projection along the crankshaft axis, the projected area of ​​the first back pressure space is S1, and the projected area of ​​the moving scroll plate is S2, wherein S1 and S2 satisfy the relationship: 0.089≤S1 / S2≤0.298; the displacement V of the compressor satisfies the relationship: 6cm 3 ≤V≤10cm 3 The maximum radial dimension D1 of the moving scroll disk along the crankshaft radial direction satisfies the following relationship: 76mm≤D1≤84mm.

[0013] Furthermore, the minimum flow cross-sectional area S3 of the first channel satisfies the following relationship: 0.03mm 2 ≤S3≤0.12mm 2 The minimum flow cross-sectional area S4 of the second channel satisfies the following relationship: S4 ≥ 0.06 mm 2 .

[0014] Furthermore, when the minimum flow cross-sectional area S4 of the second channel satisfies the relationship: 0.06mm 2≤S4≤0.4mm 2 At that time, the minimum flow cross-sectional area S3 of the first channel satisfies the relationship: 0.03mm 2 ≤S3≤0.07mm 2 And S1 and S2 satisfy the relationship: 0.133≤S1 / S2≤0.179.

[0015] Furthermore, when the minimum flow cross-sectional area S4 of the second channel satisfies the relationship: 0.06mm 2 ≤S4≤0.4mm 2 At that time, the minimum flow cross-sectional area S3 of the first channel satisfies the relationship: 0.07mm 2 ≤S3≤0.12mm 2 And S1 and S2 satisfy the relationship: 0.089≤S1 / S2≤0.133.

[0016] Furthermore, when the minimum flow cross-sectional area S4 of the second channel satisfies the relationship: S4 > 0.4 mm 2 At that time, the minimum flow cross-sectional area S3 of the first channel satisfies the relationship: 0.07mm 2 ≤S3≤0.12mm 2 And S1 and S2 satisfy the relationship: 0.133≤S1 / S2≤0.179.

[0017] Furthermore, when the minimum flow cross-sectional area S4 of the second channel satisfies the relationship: S4 > 0.4 mm 2 At that time, the minimum flow cross-sectional area S3 of the first channel satisfies the relationship: 0.03mm 2 ≤S3≤0.07mm 2 And S1 and S2 satisfy the relationship: 0.179≤S1 / S2≤0.298.

[0018] Furthermore, the first channel extends radially along the crankshaft, and the extension length D2 of the first channel satisfies the relationship: 2mm≤D2≤5mm.

[0019] Furthermore, the first vortex tooth is spirally arranged around the outer periphery of the first bearing hole, and the stationary vortex disk is provided with an air intake channel, which is connected to the air intake pipe;

[0020] The second channel is disposed on the stationary scroll plate. The second channel includes a first flow section, a second flow section, and a third flow section. The first flow section and the third flow section both extend along the axial direction of the crankshaft. The second flow section extends from the outer edge of the stationary scroll plate toward the inner side of the stationary scroll plate and communicates with the first flow section and the third flow section. The first flow section is closer to the crankshaft than the third flow section. The first flow section communicates with the compression chamber, and the third flow section communicates with the second back pressure space.

[0021] Starting from the center point O1 of the first bearing hole, draw a line O1A connecting it to the central axis of the air intake channel, and starting from the center point O1 of the first bearing hole, draw a line O1B connecting it to the center of the first flow section. Along the spiral winding direction of the first vortex tooth, the included angle θ1 between O1A and O1B satisfies the relationship: 240°≤θ1≤320°.

[0022] Furthermore, the second vortex tooth portion is spirally arranged around the outer periphery of the eccentric bearing hole;

[0023] The second channel is disposed on the moving scroll disk. The second channel includes a fourth flow section and a fifth flow section. The fourth flow section extends along the axial direction of the crankshaft and communicates with the compression chamber. The fifth flow section extends from the outer edge of the moving scroll disk toward the inner side of the moving scroll disk and communicates with the fourth flow section and the second back pressure space.

[0024] Starting from the center point O2 of the eccentric bearing hole, draw a line O2C connecting it to the farthest point of the second vortex tooth along the radial direction of the crankshaft. Starting from the center point O2 of the eccentric bearing hole, draw a line O2D connecting it to the center of the fourth flow section. Along the spiral winding direction of the second vortex tooth, the included angle θ2 between O2C and O2D satisfies the relationship: 250°≤θ2≤330°.

[0025] Furthermore, the stationary scroll plate has a first plane on the side near the moving scroll plate, and the support has a second plane on the side near the moving scroll plate. A receiving groove is formed on the second plane, and a first boss and a second boss are provided in the receiving groove. The first boss and the second boss are arranged around the circumference of the support and are arranged in sequence from the inside to the outside along the radial direction of the crankshaft. Along the axial direction of the crankshaft, the distance between the first boss and the second plane is greater than the distance between the second boss and the second plane.

[0026] The second bearing hole passes through the first boss, the seal is located between the moving scroll and the first boss, and the first plane is in contact with the second plane; when the moving scroll moves along the crankshaft axis toward a direction away from the stationary scroll, the end face of the second boss near the moving scroll is in contact with the side of the moving scroll away from the stationary scroll.

[0027] Furthermore, a first annular groove is provided on the side of the first boss near the moving scroll plate. The first annular groove is located on the outer periphery of the second bearing hole and is spaced apart from the second bearing hole. The first annular groove is arranged around the second bearing hole in the circumferential direction. The sealing element is provided in the first annular groove. The sealing element includes an annular sealing ring.

[0028] The first annular groove divides the end face of the first protrusion near the moving scroll into a first end face and a second end face. The first end face is closer to the crankshaft than the second end face, and the distance between the first end face and the moving scroll is greater than the distance between the second end face and the moving scroll.

[0029] Furthermore, a second annular groove is provided on the side of the moving scroll disk near the bracket. The second annular groove is located on the outer periphery of the eccentric bearing hole and is spaced apart from the eccentric bearing hole. The second annular groove is arranged around the circumference of the eccentric bearing hole. The sealing element is provided in the second annular groove. The sealing element includes an annular sealing ring.

[0030] The second annular groove divides the end face of the moving scroll disk near the bracket into a third end face and a fourth end face. The third end face is closer to the crankshaft than the fourth end face, and the distance between the third end face and the bracket is greater than the distance between the fourth end face and the bracket.

[0031] On the other hand, this application also provides an air conditioning system, which includes the compressor described above for use in air conditioning systems.

[0032] Since the first back pressure space in this application is connected to the accommodating cavity, when the accommodating cavity is in a high-pressure environment, the pressure in the first back pressure space is also high. The pressure in the compression cavity corresponding to the first back pressure space is relatively high during the later stages of compression and the exhaust stage. Therefore, the high pressure in the first back pressure space will cancel out the axial force exerted by the gas in the compression cavity on the moving scroll plate, thereby preventing the moving scroll plate from moving away from the stationary scroll plate along the crankshaft axis and causing gas leakage in the compression cavity. Furthermore, since the first channel in this application connects to the first back pressure space and the second back pressure space, and the second channel connects to the compression chamber and the second back pressure space, the gas in the compression chamber can be guided into the second back pressure space through the second channel to increase the pressure in the second back pressure space. This causes the back of the moving scroll to be subjected to an upward back pressure, thereby inhibiting the moving scroll from moving away from the stationary scroll. At the same time, the pressure in the first back pressure space is transmitted to the second back pressure space through the first channel, so that the pressure in the second back pressure space is jointly determined by the pressure in the compression chamber and the pressure in the first back pressure space, further regulating the pressure in the second back pressure space, thereby better preventing the moving scroll from moving away from the stationary scroll. Based on this, the back pressure in the first and second back pressure spaces can be easily maintained within a reasonable range, neither too low to prevent the moving scroll and the stationary scroll from fitting together, nor too high to cause wear due to excessive contact between the moving scroll and the stationary scroll, effectively improving the performance and reliability of the compressor. Attached Figure Description

[0033] 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:

[0034] Figure 1 This is a cross-sectional view of the compressor disclosed in an embodiment of this application;

[0035] Figure 2 This is an exploded view of the pump body assembly disclosed in the embodiments of this application;

[0036] Figure 3 This is a cross-sectional view of the pump body assembly disclosed in an embodiment of this application;

[0037] Figure 4 This is a cross-sectional view of the moving scroll disk and the support (with a first annular groove) being assembled according to an embodiment of this application;

[0038] Figure 5 This is a cross-sectional view of the moving scroll disk (with a second annular groove) and the bracket as disclosed in the embodiments of this application.

[0039] Figure 6This is a schematic diagram of the structure of the second channel inlet being disposed on the static vortex disk, as disclosed in an embodiment of this application;

[0040] Figure 7 This is a schematic diagram of the structure of the second channel inlet disposed on the moving vortex disk as disclosed in the embodiments of this application;

[0041] Figure 8 This is a schematic diagram of the structure of the stationary vortex disk disclosed in the embodiments of this application;

[0042] Figure 9 This is a schematic diagram of the structure of the stent disclosed in the embodiments of this application.

[0043] The above figures include the following reference numerals:

[0044] 10. Housing; 101. Receptacle; 102. Oil reservoir; 11. Intake pipe; 12. Exhaust pipe; 20. Motor; 21. Rotor; 22. Stator; 30. Pump assembly; 301. Compression chamber; 31. Crankshaft; 311. First shaft section; 312. Eccentric section; 313. Second shaft section; 32. Stationary scroll plate; 321. First scroll tooth section; 322. First bearing section; 323. First bearing hole; 324. Intake channel; 325. First plane; 33. Moving scroll plate; 331. Second scroll tooth section; 332. Eccentric bearing hole; 333. Second annular groove; 334. 335. Third end face; 34. Fourth end face; 35. Seal; 36. Annular seal; 37. Anti-rotation component; 38. Bracket; 39. Second bearing part; 30. Second bearing hole; 31. Second plane; 32. Accommodating groove; 33. First boss; 34. First end face; 35. Second end face; 36. Second boss; 36. First annular groove; 40. First back pressure space; 50. Second back pressure space; 61. First channel; 72. Second channel; 73. First flow section; 74. Second flow section; 75. Third flow section; 76. Fourth flow section. Detailed Implementation

[0045] 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.

[0046] 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.

[0047] 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.

[0048] See Figures 1 to 9 As shown in the embodiments of this application, a compressor for use in an air conditioning system is provided. The compressor includes a vertical variable frequency scroll compressor and further includes a housing 10, a motor 20, and a pump assembly 30.

[0049] 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, an anti-rotation component 35, and a support. The crankshaft 31 is rotatably mounted in the housing 101, passing through the stationary scroll 32, the moving scroll 33, the seal 34, the anti-rotation component 35, and the bracket 36. The stationary scroll 32 has a first scroll tooth 321 on the side near the moving scroll 33, and the moving scroll 33 has a second scroll tooth 331 that meshes with the first scroll tooth 321. The meshing of the first scroll tooth 321 and the second scroll tooth 331 forms a compression chamber 301. An air intake is provided on the housing 10. Pipe 11 and exhaust pipe 12, intake pipe 11 is connected to pump body assembly 30, exhaust pipe 12 is connected to accommodating cavity 101, crankshaft 31 includes a first shaft section 311, an eccentric section 312 and a second shaft section 313 arranged sequentially along its own axis, stationary scroll plate 32 is provided with a first bearing part 322 on the side opposite to the moving scroll plate 33, the first bearing part 322 has a first bearing hole 323, bracket 36 is provided with a second bearing part 361 on the side opposite to the moving scroll plate 33, the second bearing part 361 The rotating scroll 33 has a second bearing hole 362 and an eccentric bearing hole 332. The motor 20 is mounted on the first shaft section 311 via the rotor 21. The stationary scroll 32 is mounted on the first shaft section 311 or the second shaft section 313 via the first bearing hole 323. The rotating scroll 33 is mounted on the eccentric section 312 via the eccentric bearing hole 332. The bracket 36 is mounted on the second shaft section 313 or the first shaft section 311 via the second bearing hole 362. The anti-rotation component 35 is disposed between the rotating scroll 33 and the bracket 36.

[0050] The sealing element 34 is disposed between the moving scroll plate 33 and the bracket 36. The side of the sealing element 34 near the crankshaft 31 forms a first back pressure space 40 between the moving scroll plate 33 and the bracket 36, and the side of the sealing element 34 away from the crankshaft 31 forms a second back pressure space 50 between the moving scroll plate 33, the stationary scroll plate 32, and the bracket 36. Both the first back pressure space 40 and the second back pressure space 50 are arranged circumferentially around the crankshaft 31. The pump body assembly 30 has a first channel 60 and a second channel 70. The first channel 60 connects to the first back pressure space 40 and the second back pressure space 50, the second channel 70 connects to the compression chamber 301 and the second back pressure space 50, and the first back pressure space 40 connects to the accommodating cavity 101; within the projection along the crankshaft 31 axial direction, the projected area of ​​the first back pressure space 40 is S1, and the projected area of ​​the moving scroll plate 33 is S2, wherein S1 and S2 satisfy the relationship: 0.089≤S1 / S2≤0.298; the compressor displacement V satisfies the relationship: 6cm 3 ≤V≤10cm 3 The maximum radial dimension D1 of the moving scroll disk 33 along the crankshaft 31 satisfies the relationship: 76mm≤D1≤84mm. For example, S1 / S2 in this embodiment can be set to 0.089, 0.1, 0.12, 0.14, 0.16, 0.18, 0.20, 0.22, 0.24, 0.26, 0.28, 0.29, 0.298, etc.

[0051] 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 and appendix Figure 3 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.

[0052] It is worth noting that, see Figure 1 as well as Figure 3 As shown in the embodiments illustrated in this application, the first channel 60 is located on the side of the moving scroll plate 33 away from the stationary scroll plate 32. Of course, in other embodiments not shown in this application, the first channel 60 may also be disposed on other components of the pump body assembly 30. This application does not make specific limitations, as long as the first channel 60 is connected to the first back pressure space 40 and the second back pressure space 50.

[0053] Similarly, see Figure 1 as well as Figure 3As shown in the embodiments illustrated in this application, the second channel 70 is disposed on the stationary vortex disk 32. Of course, in other embodiments not shown in this application, the second channel 70 may also be disposed on the moving vortex disk 33. This application does not make specific limitations here, as long as the second channel 70 is connected to the compression chamber 301 and the second back pressure space 50.

[0054] In this embodiment, during the actual manufacturing of the compressor, both the motor 20 and the pump assembly 30 can be installed inside the accommodating cavity 101, with the pump assembly 30 positioned closer to the bottom of the accommodating cavity 101 than the motor 20. Since the moving scroll plate 33 is fitted onto the eccentric section 312 via 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 section 312 to rotate, thereby causing the moving scroll plate 33 to rotate synchronously. This, in turn, causes the stationary scroll plate 32 to rotate relative to the moving scroll plate 33, compressing the refrigerant entering the compression cavity 301 from the intake pipe 11, thus achieving a change in the volume of the compression cavity 301. After the pump assembly 30 completes compression, it discharges the gas into the accommodating cavity 101 and then out of the casing 10 through the exhaust pipe 12. During the operation of the pump assembly 30, the compression chamber 301 is divided into multiple sub-chambers by the first scroll tooth portion 321 and the second scroll tooth portion 331, and the pressure difference between the sub-chambers is small, resulting in less leakage in the compression chamber 301 and effectively improving the energy efficiency of the compressor. Meanwhile, in this embodiment, the stationary scroll plate 32 has a first bearing portion 322, the bracket 36 has a second bearing portion 361, and the pump assembly 30 is closer to the bottom of the receiving cavity 101 than the motor 20; that is, the compressor adopts a bottom-mounted pump assembly 30 structure. Thus, the presence of the first bearing portion 322 and the second bearing portion 361 can support the crankshaft 31, eliminating the need for an additional bearing on the other side of the motor 20 to support the crankshaft 31. 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, ensuring reliable compressor operation without the need for additional bushings. The overall structure is simple and the manufacturing cost is low.

[0055] However, the establishment of back pressure in the above-described compressor structure is more complex. Similar to existing scroll compressors, the compressor in this embodiment also introduces an intermediate pressure between the intake and exhaust pressures into the back pressure chamber to counteract the axial force and torque exerted on the moving scroll 33 by the gas force in the compression chamber 301. However, the difference is that, since the moving scroll 33 in this embodiment is provided with an eccentric bearing hole 332, and the crankshaft 31 is provided with an oil passage to guide lubricating oil into the eccentric bearing hole 332 to lubricate the bearing, after lubricating the eccentric bearing hole 332, the lubricating oil will then flow into the back pressure chamber. At this time, the pressure in the back pressure chamber is determined by the intermediate pressure between the intake and exhaust pressures and the high pressure carried by the lubricating oil. If the lubricating oil is not isolated in a segmented area, the oil pressure influence range will be too large, which will result in an excessively high back pressure. In response to this situation, the solution in this embodiment is to provide a seal 34 between the moving scroll 33 and the bracket 36. The seal 34 is used to isolate the intermediate pressure and the high pressure, so that the intermediate pressure and the high pressure are located in different areas of the back pressure chamber. The high pressure is located on the side of the seal 34 closer to the crankshaft 31, that is, the high pressure is located in the first back pressure space 40, while the intermediate pressure is located in the second back pressure space 50.

[0056] Meanwhile, since the first back pressure space 40 in this embodiment is connected to the accommodating cavity 101, when the accommodating cavity 101 is in a high-pressure environment, the pressure in the first back pressure space 40 is also high. The pressure in the compression cavity 301 corresponding to the first back pressure space 40 is relatively high during the later stages of compression and the exhaust stage. Therefore, the high pressure in the first back pressure space 40 will cancel out the axial force exerted by the gas in the compression cavity 301 on the moving scroll plate 33, thereby preventing the moving scroll plate 33 from moving axially away from the stationary scroll plate 32 along the crankshaft 31 and causing gas leakage in the compression cavity 301. Furthermore, since the first channel 60 in this embodiment is connected to the first back pressure space 40 and the second back pressure space 50, and the second channel 70 is connected to the compression chamber 301 and the second back pressure space 50, the gas in the compression chamber 301 can be guided into the second back pressure space 50 through the second channel 70 to increase the pressure of the second back pressure space 50. This causes the back of the moving scroll plate 33 to be subjected to an upward back pressure, thereby inhibiting the moving scroll plate 33 from moving away from the stationary scroll plate 32. At the same time, the pressure of the first back pressure space 40 is transmitted to the second back pressure space 50 through the first channel 60, so that the pressure of the second back pressure space 50 is determined by the pressure of the compression chamber 301 and the pressure of the first back pressure space 40. This further regulates the pressure of the second back pressure space 50, thereby better preventing the moving scroll plate 33 from moving away from the stationary scroll plate 32. Based on this, the back pressure of the first back pressure space 40 and the second back pressure space 50 can be kept within a reasonable range. It is not too small so that the moving scroll 33 and the stationary scroll 32 cannot fit together, nor is it too large so that the moving scroll 33 and the stationary scroll 32 will wear due to excessive contact. This effectively improves the performance and reliability of the compressor.

[0057] Furthermore, since the first back pressure space 40 in this embodiment is connected to the accommodating cavity 101, the larger the area of ​​the first back pressure space 40, the greater the back pressure that the first back pressure space 40 can provide to the moving scroll disk 33. Based on this, in this embodiment, by making the ratio between the projected area S1 of the first back pressure space 40 and the projected area S2 of the moving scroll disk 33 greater than or equal to 0.089 and less than or equal to 0.298, it can be ensured that the back pressure that the first back pressure space 40 can provide to the moving scroll disk 33 is within a suitable range and will not be too large or too small. When S1 / S2 is less than 0.089, the projected area of ​​the first back pressure space 40 is small, resulting in a small back pressure that the first back pressure space 40 can provide. The small back pressure is insufficient to make the moving scroll plate 33 and the stationary scroll plate 32 fit together, which leads to serious gas leakage in the compression chamber 301. When S1 / S2 is greater than 0.298, the projected area of ​​the first back pressure space 40 is large, resulting in excessive pressure in the first back pressure space 40, which leads to excessive fit between the moving scroll plate 33 and the stationary scroll plate 32, causing severe wear on the moving scroll plate 33 and the stationary scroll plate 32.

[0058] Specifically, in this embodiment, the displacement V of the compressor satisfies the following relationship: 6cm 3 ≤V≤10cm 3 For example, V can be set to 6cm. 3 6.5cm 3 7cm 3 7.5cm 3 8cm 3 8.5cm 3 9cm 3 9.5cm 3 10cm 3 etc. When V is less than 6cm 3 When the compressor displacement is too small, the internal volume of the compression chamber 301 is relatively small, which leads to undercompression under certain operating conditions and a decrease in compressor efficiency; when V is greater than 10cm 3 At that time, the compressor was relatively large, which increased the manufacturing cost of the compressor.

[0059] Specifically, in this embodiment, the maximum radial dimension D1 of the moving scroll disk 33 along the crankshaft 31 (see...) Figures 4 to 5 As shown, the following relationship is satisfied: 76mm≤D1≤84mm. For example, D1 can be set to 76mm, 77mm, 78mm, 79mm, 80mm, 81mm, 82mm, 83mm, 84mm, etc.

[0060] Specifically, the moving scroll plate 33 is used to house the second scroll tooth 331 and needs to seal and cover the first scroll tooth 321 of the stationary scroll plate 32. The maximum radial dimension of the moving scroll plate 33 is related to the bore diameter of the eccentric bearing hole 332, the tooth thickness of the second scroll tooth 331, the eccentricity of the eccentric section 312, the number of scrolls of the second scroll tooth 331, and the sealing width. The smaller these parameters are, the smaller the maximum radial dimension of the moving scroll 33. However, if the diameter of the eccentric bearing bore 332 is too small, it will cause excessive surface pressure on the eccentric section 312, leading to reliability problems. If the tooth thickness of the second scroll tooth 331 is too small, it will cause deformation of the second scroll tooth 331, resulting in the risk of meshing friction or even breakage. If the eccentricity is too small, it will cause excessive surface pressure on the first shaft section 311 and the second shaft section 313 of the crankshaft 31, leading to reliability problems. If the number of scroll turns of the second scroll tooth 331 is small, it will be difficult to increase the volume ratio, which will make the compressor prone to undercompression losses and reduce energy efficiency. If the sealing width is too small, it will cause excessive leakage and reduce the energy efficiency of the compressor. Therefore, the maximum radial dimension of the moving scroll 33 is limited. In this embodiment, the maximum radial dimension D1 of the moving scroll plate 33 must be greater than or equal to 76mm; otherwise, the energy efficiency and reliability of the compressor will be significantly affected. The larger the maximum radial dimension of the moving scroll plate 33, the larger the maximum radial dimension of the entire pump body assembly 30 will be, and more materials will be used, which will reduce the cost-effectiveness of the compressor. Therefore, in this embodiment, the maximum radial dimension D1 of the moving scroll plate 33 must be less than or equal to 84mm.

[0061] Furthermore, in this embodiment, the minimum flow cross-sectional area S3 of the first channel 60 satisfies the relationship: 0.03mm. 2 ≤S3≤0.12mm 2 For example, S3 can be set to 0.03mm. 2 0.04mm 2 0.06mm 2 0.08mm 2 0.1mm 2 0.12mm 2 The minimum flow cross-sectional area S4 of the second channel 70 satisfies the following relationship: S4 ≥ 0.06 mm 2 For example, S4 can be set to 0.06mm. 2 0.08mm 2 0.1mm 2 0.15mm 2 0.2mm 2 0.25mm 2It should be noted that, in this embodiment, "the flow cross-sectional area of ​​the first channel 60" refers to the area of ​​the cross-section obtained by cutting the first channel 60 along the direction perpendicular to the flow of the fluid; "the flow cross-section of the second channel 70" refers to the area of ​​the cross-section obtained by cutting the second channel 70 along the direction perpendicular to the flow of the fluid.

[0062] Specifically, in this embodiment, the pressure in the second back pressure space 50 is adjusted by the pressure in the compression chamber 301 and the pressure in the first back pressure space 40. The second back pressure space 50 is connected to the first back pressure space 40 via the first channel 60 and to the compression chamber 301 via the second channel 70. Therefore, the flow area of ​​the first channel 60 and the second channel 70 can control the pressure entering the second back pressure space 50. A larger flow area in the first channel 60 will increase the pressure in the second back pressure space 50. Simultaneously, the flow area of ​​the first channel 60 also affects the oil intake of the entire pump assembly 30. When the minimum flow cross-section S3 of the first channel 60 is greater than 0.12 mm... 2 When the oil intake of the pump body assembly 30 is excessive, the compressor's energy efficiency is reduced. This occurs when the minimum flow cross-section S3 of the first channel 60 is less than 0.03 mm. 2 At this time, the oil inlet volume of the pump body assembly 30 is too small, resulting in insufficient lubrication. Therefore, in this embodiment, the minimum flow cross-sectional area S3 of the first channel 60 is made to satisfy the relationship: 0.03mm. 2 ≤S3≤0.12mm 2 This effectively ensures the compressor's energy efficiency and sufficient lubrication; when the minimum flow cross-section S4 of the second channel 70 is less than 0.06mm. 2 If the flow area of ​​the second channel 70 is too small, the pressure in the second back pressure space 50 will easily decrease. The flow area of ​​the second channel 70 affects the lubrication in the compression chamber 301. When the minimum flow cross section S4 of the second channel 70 is too large, the amount of oil entering the compression chamber 301 will increase, which will affect the cooling capacity. In severe cases, it may even cause liquid hammer and damage to the pump body.

[0063] Furthermore, in this embodiment, the minimum flow cross-sectional area S4 of the second channel 70 satisfies the relationship: 0.06mm 2 ≤S4≤0.4mm 2 For example, S4 can be set to 0.06mm. 2 0.08mm 2 0.1mm 2 0.15mm 2 0.2mm 2 0.25mm 2 0.3mm 2 0.35mm 2 0.4mm 2The minimum flow cross-sectional area S3 of the first channel 60 satisfies the following relationship: 0.03mm² 2 ≤S3≤0.07mm 2 For example, S3 can be set to 0.03mm. 2 0.04mm 2 0.05mm 2 0.06mm 2 0.07mm 2 And S1 and S2 satisfy the relationship: 0.133≤S1 / S2≤0.179. For example, S1 / S2 can be set to 0.133, 0.135, 0.140, 0.145, 0.150, 0.155, 0.160, 0.165, 0.170, 0.175, 0.179, etc.

[0064] Specifically, in this embodiment, the pressure of the second back pressure space 50 can be adjusted by the flow area of ​​the first channel 60, the flow area of ​​the second channel 70, and the ratio of S1 / S2. A larger flow area of ​​the first channel 60 will increase the pressure of the second back pressure space 50. The flow area of ​​the first channel 60 also affects the oil intake of the entire pump assembly 30. However, if the flow area of ​​the first channel 60 is too large, the oil intake will be excessive, affecting the compressor's energy efficiency; conversely, if the flow area of ​​the first channel 60 is too small, the oil intake will be insufficient, leading to inadequate lubrication. Therefore, the flow area of ​​the first channel 60 is relatively fixed. In this embodiment, the minimum flow cross-sectional area S4 of the second channel 70 satisfies the relationship: 0.06mm. 2 ≤S4≤0.4mm 2 Based on this, the minimum flow cross-sectional area S3 of the first channel 60 satisfies the relationship: 0.03mm. 2 ≤S3≤0.07mm 2This ensures that the pressure in the second back pressure space 50 and the oil flow rate in the first channel 60 are within the required range. It is understood that, given the flow area of ​​the first channel 60 and the flow area of ​​the second channel 70, the ratio of S1 / S2 is determined to ensure the moving scroll plate 33 has optimal back pressure. In this embodiment, by ensuring that S1 and S2 satisfy the relationship: 0.133≤S1 / S2≤0.179, the back pressure provided by the first back pressure space 40 to the moving scroll plate 33 is within a suitable range and is neither too high nor too low. When S1 / S2 is less than 0.133, the projected area of ​​the first back pressure space 40 is small, resulting in a small back pressure that the first back pressure space 40 can provide. The small back pressure is insufficient to make the moving scroll plate 33 and the stationary scroll plate 32 fit together, which leads to serious gas leakage in the compression chamber 301. When S1 / S2 is greater than 0.179, the projected area of ​​the first back pressure space 40 is large, resulting in excessive pressure in the first back pressure space 40, which leads to excessive fit between the moving scroll plate 33 and the stationary scroll plate 32, causing severe wear on the moving scroll plate 33 and the stationary scroll plate 32.

[0065] Furthermore, in this embodiment, the minimum flow cross-sectional area S4 of the second channel 70 satisfies the relationship: 0.06mm 2 ≤S4≤0.4mm 2 For example, S4 can be set to 0.06mm. 2 0.08mm 2 0.1mm 2 0.15mm 2 0.2mm 2 0.25mm 2 0.3mm 2 0.35mm 2 0.4mm 2 The minimum flow cross-sectional area S3 of the first channel 60 satisfies the following relationship: 0.07mm² 2 ≤S3≤0.12mm 2 For example, S3 can be set to 0.07mm. 2 0.08mm 2 0.09mm 2 0.1mm 2 0.11mm 2 0.12mm 2 And S1 and S2 satisfy the relationship: 0.089≤S1 / S2≤0.133. For example, S1 / S2 can be set to 0.089, 0.090, 0.092, 0.094, 0.096, 0.098, 0.1, 0.11, 0.12, 0.13, 0.133, etc.

[0066] Specifically, in this embodiment, the pressure of the second back pressure space 50 can be adjusted by the flow area of ​​the first channel 60, the flow area of ​​the second channel 70, and the ratio of S1 / S2. A larger flow area of ​​the first channel 60 will increase the pressure of the second back pressure space 50. The flow area of ​​the first channel 60 also affects the oil intake of the entire pump assembly 30. However, if the flow area of ​​the first channel 60 is too large, the oil intake will be excessive, affecting the compressor's energy efficiency; conversely, if the flow area of ​​the first channel 60 is too small, the oil intake will be insufficient, leading to inadequate lubrication. Therefore, the flow area of ​​the first channel 60 is relatively fixed. In this embodiment, the minimum flow cross-sectional area S4 of the second channel 70 satisfies the relationship 0.06mm. 2 ≤S4≤0.4mm 2 Based on this, the minimum flow cross-sectional area S3 of the first channel 60 satisfies the relationship: 0.07mm. 2 ≤S3≤0.12mm 2 This ensures that the pressure in the second back pressure space 50 and the oil flow rate in the first channel 60 are within the required range. It is understood that, given the flow areas of the first channel 60 and the second channel 70, the ratio of S1 / S2 is determined to ensure the moving scroll plate 33 has optimal back pressure. In this embodiment, by ensuring that S1 and S2 satisfy the relationship: 0.089≤S1 / S2≤0.133, the back pressure provided by the first back pressure space 40 to the moving scroll plate 33 is within a suitable range and is neither too high nor too low. When S1 / S2 is less than 0.089, the projected area of ​​the first back pressure space 40 is small, resulting in a small back pressure that the first back pressure space 40 can provide. The small back pressure is insufficient to make the moving scroll plate 33 and the stationary scroll plate 32 fit together, which leads to serious gas leakage in the compression chamber 301. When S1 / S2 is greater than 0.133, the projected area of ​​the first back pressure space 40 is large, resulting in excessive pressure in the first back pressure space 40, which leads to excessive fit between the moving scroll plate 33 and the stationary scroll plate 32, causing severe wear on the moving scroll plate 33 and the stationary scroll plate 32.

[0067] Furthermore, in this embodiment, the minimum flow cross-sectional area S4 of the second channel 70 satisfies the relationship: S4 > 0.4 mm. 2 For example, S4 can be set to 0.42mm. 2 0.44mm 2 0.46mm 2 0.48mm 2 0.5mm 2 0.52mm 2 0.54mm 2 0.56mm 2 0.58mm 20.6mm 2 The minimum flow cross-sectional area S3 of the first channel 60 satisfies the following relationship: 0.07mm² 2 ≤S3≤0.12mm 2 For example, S3 can be set to 0.07mm. 2 0.08mm 2 0.09mm 2 0.1mm 2 0.11mm 2 0.12mm 2 Furthermore, S1 and S2 satisfy the relationship: 0.133≤S1 / S2≤0.179. For example, S1 / S2 can be set to 0.133, 0.135, 0.140, 0.145, 0.150, 0.155, 0.160, 0.165, 0.170, 0.175, 0.179, etc.

[0068] Specifically, in this embodiment, the pressure in the second back pressure space 50 can be adjusted by the flow area of ​​the first channel 60, the flow area of ​​the second channel 70, and the ratio of S1 / S2. A larger flow area in the first channel 60 will increase the pressure in the second back pressure space 50. The flow area of ​​the first channel 60 also affects the oil intake of the entire pump assembly 30. However, if the flow area of ​​the first channel 60 is too large, the oil intake will be excessive, affecting the compressor's energy efficiency; conversely, if the flow area of ​​the first channel 60 is too small, the oil intake will be insufficient, leading to inadequate lubrication. Therefore, the flow area of ​​the first channel 60 is relatively fixed. In this embodiment, the minimum flow cross-sectional area S4 of the second channel 70 satisfies the relationship S4 > 0.4 mm. 2 Based on this, the minimum flow cross-sectional area S3 of the first channel 60 satisfies the relationship: 0.07mm. 2 ≤S3≤0.12mm 2This ensures that the pressure in the second back pressure space 50 and the oil flow rate in the first channel 60 are within the required range. It is understood that, given the flow area of ​​the first channel 60 and the flow area of ​​the second channel 70, the ratio of S1 / S2 is determined to ensure the moving scroll plate 33 has optimal back pressure. In this embodiment, by ensuring that S1 and S2 satisfy the relationship: 0.133≤S1 / S2≤0.179, the back pressure provided by the first back pressure space 40 to the moving scroll plate 33 is within a suitable range and is neither too high nor too low. When S1 / S2 is less than 0.133, the projected area of ​​the first back pressure space 40 is small, resulting in a small back pressure that the first back pressure space 40 can provide. The small back pressure is insufficient to make the moving scroll plate 33 and the stationary scroll plate 32 fit together, which leads to serious gas leakage in the compression chamber 301. When S1 / S2 is greater than 0.179, the projected area of ​​the first back pressure space 40 is large, resulting in excessive pressure in the first back pressure space 40, which leads to excessive fit between the moving scroll plate 33 and the stationary scroll plate 32, causing severe wear on the moving scroll plate 33 and the stationary scroll plate 32.

[0069] Furthermore, in this embodiment, the minimum flow cross-sectional area S4 of the second channel 70 satisfies the relationship: S4 > 0.4 mm. 2 For example, S4 can be set to 0.42mm. 2 0.44mm 2 0.46mm 2 0.48mm 2 0.5mm 2 0.52mm 2 0.54mm 2 0.56mm 2 0.58mm 2 0.6mm 2 The minimum flow cross-sectional area S3 of the first channel 60 satisfies the following relationship: 0.03mm² 2 ≤S3≤0.07mm 2 For example, S3 can be set to 0.03mm. 2 0.04mm 2 0.05mm 2 0.06mm 2 0.07mm 2 And S1 and S2 satisfy the relationship: 0.179≤S1 / S2≤0.298. For example, S1 / S2 can be set to 0.179, 0.180, 0.185, 0.190, 0.195, 0.200, 0.220, 0.240, 0.260, 0.280, 0.290, 0.298, etc.

[0070] Specifically, in this embodiment, the pressure in the second back pressure space 50 can be adjusted by the flow area of ​​the first channel 60, the flow area of ​​the second channel 70, and the ratio of S1 / S2. A larger flow area in the first channel 60 will increase the pressure in the second back pressure space 50. The flow area of ​​the first channel 60 also affects the oil intake of the entire pump assembly 30. However, if the flow area of ​​the first channel 60 is too large, the oil intake will be excessive, affecting the compressor's energy efficiency; conversely, if the flow area of ​​the first channel 60 is too small, the oil intake will be insufficient, leading to inadequate lubrication. Therefore, the flow area of ​​the first channel 60 is relatively fixed. In this embodiment, the minimum flow cross-sectional area S4 of the second channel 70 satisfies the relationship S4 > 0.4 mm. 2 Based on this, the minimum flow cross-sectional area S3 of the first channel 60 satisfies the relationship: 0.03mm. 2 ≤S3≤0.07mm 2 This ensures that the pressure in the second back pressure space 50 and the oil flow rate in the first channel 60 are within the required range. It is understood that, given the flow areas of the first channel 60 and the second channel 70, the ratio of S1 / S2 is determined to ensure the moving scroll plate 33 has optimal back pressure. In this embodiment, by ensuring that S1 and S2 satisfy the relationship: 0.179 ≤ S1 / S2 ≤ 0.298, the back pressure provided by the first back pressure space 40 to the moving scroll plate 33 is within a suitable range and is neither too high nor too low. When S1 / S2 is less than 0.179, the projected area of ​​the first back pressure space 40 is small, resulting in a small back pressure that the first back pressure space 40 can provide. The small back pressure is insufficient to make the moving scroll plate 33 and the stationary scroll plate 32 fit together, which leads to serious gas leakage in the compression chamber 301. When S1 / S2 is greater than 0.298, the projected area of ​​the first back pressure space 40 is large, resulting in excessive pressure in the first back pressure space 40, which leads to excessive fit between the moving scroll plate 33 and the stationary scroll plate 32, causing severe wear on the moving scroll plate 33 and the stationary scroll plate 32.

[0071] Further, see Figure 1 as well as Figure 3 As shown, in this embodiment, the first channel 60 extends radially along the crankshaft 31, and the extension length D2 of the first channel 60 (as shown) Figure 3 As shown, the following relationship is satisfied: 2mm≤D2≤5mm. For example, D2 can be set to 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, etc.

[0072] Specifically, since the lubricating oil in the first back pressure space 40 can enter the second back pressure space 50 through the first channel 60, the amount of lubricating oil entering is related not only to the flow area of ​​the first channel 60 but also to its flow length. The amount of lubricating oil flowing out through the first channel 60 is inversely proportional to its flow length; the longer the flow length of the first channel 60, the less lubricating oil flows out. Therefore, given a fixed minimum flow cross-section of the first channel 60, its flow length should also be adjusted accordingly. Thus, in this embodiment, by ensuring that the extension length D2 of the first channel 60 satisfies the relationship: 2mm ≤ D2 ≤ 5mm, not only can lubricating oil flow into the second back pressure space 50 through the first channel 60, but excessive lubricating oil can also be prevented, effectively ensuring the reliability and stability of the compressor operation.

[0073] Further, see Figure 3 as well as Figure 6 As shown, in this embodiment, the first scroll tooth 321 is spirally arranged around the outer periphery of the first bearing hole 323. An intake channel 324 is provided on the stationary scroll 32, which is connected to the intake pipe 11. A second channel 70 is provided on the stationary scroll 32, and includes a first flow section 71, a second flow section 72, and a third flow section 73. The first flow section 71 and the third flow section 73 both extend axially along the crankshaft 31. The second flow section 72 extends from the outer edge of the stationary scroll 32 toward the inner side of the stationary scroll 32 and connects with the first flow section 71 and the third flow section 73. The first flow section 71 is closer to the crankshaft 31 than the third flow section 73. 1. The first flow section 71 is connected to the compression chamber 301, and the third flow section 73 is connected to the second back pressure space 50. A line O1A is drawn connecting the center point O1 of the first bearing hole 323 to the central axis of the suction channel 324, and another line O1B is drawn connecting the center point O1 of the first bearing hole 323 to the center of the first flow section 71. Along the spiral winding direction of the first vortex tooth 321, the included angle θ1 between O1A and O1B satisfies the relationship: 240°≤θ1≤320°. For example, θ1 can be set to 240°, 250°, 260°, 270°, 280°, 290°, 300°, 310°, 320°, etc. It should be noted that the "spiral winding direction of the first vortex tooth 321" in this embodiment refers to the attached... Figure 6 The direction indicated by the letter X in the middle.

[0074] Specifically, when the second channel 70 is positioned on the stationary scroll plate 32, the gas in the compression chamber 301 will enter the second flow section 72 via the first flow section 71, and then enter the second back pressure space 50 via the third flow section 73 to increase the pressure in the second back pressure space 50. Simultaneously, the lubricating oil in the second back pressure space 50 will enter the second flow section 72 via the third flow section 73, and then enter the compression chamber 301 via the first flow section 71 to provide lubrication and reduce frictional losses between the stationary scroll plate 32 and the moving scroll plate 33. If the inlet of the first flow section 71 (i.e., the inlet of the second channel 70) is too close to the suction channel 324 along the first direction, the lubricating oil will flow towards the suction channel 324, affecting the suction process of the pump assembly 30. If the inlet of the first flow section 71 is too far from the suction channel 324, part of the compression chamber 301 will not receive effective lubrication. Therefore, when the inlet of the first flow section 71 is located at the tooth bottom of the stationary vortex disk 32, in this embodiment, by making the included angle θ1 between O1A and O1B satisfy the relationship: 240°≤θ1≤320°, it can not only ensure that all positions of the compression chamber 301 are lubricated, but also prevent the lubricating oil from flowing to the suction channel 324 and affecting the suction process.

[0075] Further, see Figure 7 As shown, in this embodiment, the second scroll tooth 331 is spirally arranged around the outer periphery of the eccentric bearing hole 332; the second channel 70 is disposed on the moving scroll disk 33, and the second channel 70 includes a fourth flow section 74 and a fifth flow section (not shown in the figure). The fourth flow section 74 extends along the axial direction of the crankshaft 31 and communicates with the compression chamber 301. The fifth flow section extends from the outer edge of the moving scroll disk 33 toward the inner side of the moving scroll disk 33 and communicates with the fourth flow section 74 and the second back pressure space 50; with the center point O2 of the eccentric bearing hole 332 as the reference. A line O2C is drawn connecting the second vortex tooth 331 to its farthest point radially along the crankshaft 31, with the center point O2 of the eccentric bearing hole 332 as the starting point, and a line O2D is drawn connecting the center of the fourth flow section 74 to the center of the eccentric bearing hole 332. Along the helical winding direction of the second vortex tooth 331, the included angle θ2 between O2C and O2D satisfies the relationship: 250°≤θ2≤330°. For example, θ2 can be set to 250°, 260°, 270°, 280°, 290°, 300°, 310°, 320°, 330°, etc. It should be noted that the "helical winding direction of the second vortex tooth 331" in this embodiment refers to the attached... Figure 7 The direction indicated by the letter Y.

[0076] Specifically, when the second channel 70 is located on the moving scroll plate 33, the gas in the compression chamber 301 will enter the fifth flow section through the fourth flow section 74, and then enter the second back pressure space 50 through the fifth flow section to increase the pressure in the second back pressure space 50. At the same time, the lubricating oil in the second back pressure space 50 will enter the fourth flow section 74 through the fifth flow section, and then enter the compression chamber 301 through the fourth flow section 74 to provide lubrication and reduce the friction loss between the stationary scroll plate 32 and the moving scroll plate 33. If the opening position of the inlet of the fourth flow section 74 (i.e., the inlet of the second channel 70) is too close to the position of the second scroll tooth 331 furthest from the eccentric bearing hole 332 along the second direction, the lubricating oil will flow to the suction channel 324, affecting the suction process of the pump body assembly 30. If the inlet of the fourth flow section 74 is too far from the position of the second scroll tooth 331 furthest from the eccentric bearing hole 332, part of the compression chamber 301 will not be effectively lubricated. Therefore, when the inlet of the fourth flow section 74 is located at the tooth bottom of the moving scroll plate 33, in this embodiment, by making the included angle θ2 between O2C and O2D satisfy the relationship: 250°≤θ2≤330°, it can not only ensure that all positions of the compression chamber 301 are lubricated, but also prevent the lubricating oil from flowing to the intake channel 324 and affecting the intake process.

[0077] Further, see Figure 3 , Figure 8 as well as Figure 9 As shown, in this embodiment, the stationary scroll plate 32 has a first plane 325 on the side near the moving scroll plate 33, and the support 36 has a second plane 363 on the side near the moving scroll plate 33. A receiving groove 364 is formed on the second plane 363, and a first boss 365 and a second boss 366 are provided in the receiving groove 364. The first boss 365 and the second boss 366 are arranged around the circumference of the support 36 and are arranged sequentially from the inside to the outside along the radial direction of the crankshaft 31. Furthermore, along the axial direction of the crankshaft 31, the first boss 365... The distance between 5 and the second plane 363 is greater than the distance between the second boss 366 and the second plane 363; wherein, the second bearing hole 362 passes through the first boss 365, the seal 34 is located between the moving scroll 33 and the first boss 365, and the first plane 325 is in contact with the second plane 363; when the moving scroll 33 moves along the crankshaft 31 in the direction away from the stationary scroll 32, the end face of the second boss 366 near the moving scroll 33 is in contact with the side of the moving scroll 33 away from the stationary scroll 32.

[0078] Specifically, after the pump body assembly 30 is installed, the first plane 325 of the stationary scroll plate 32 will fit against the second plane 363 of the bracket 36. Since the seal 34 in this embodiment is located between the moving scroll plate 33 and the first boss 365, the end face of the first boss 365 near the moving scroll plate 33, the seal 34, and the end face of the moving scroll plate 33 near the bracket 36 together achieve a sealing effect. Simultaneously, since the end face of the second boss 366 is closer to the moving scroll plate 33 in the crankshaft 31 axial direction than the end face of the first boss 365, when the moving scroll plate 33 is moved away from the stationary scroll plate 32 by the gas force of the compression chamber 301 in the axial direction, the second boss 366 can provide support for the moving scroll plate 33. In other words, during the compressor startup phase, the pressure in the back pressure chamber has not yet fully built up. At this time, the gas in the compression chamber 301 will cause axial separation of the moving scroll 33, causing the moving scroll 33 to detach from the stationary scroll 32 axially. The presence of the second protrusion 366 can promptly support the moving scroll 33 to prevent the distance between the moving scroll 33 and the stationary scroll 32 from increasing. The greater the axial distance between the moving scroll 33 and the stationary scroll 32, the more difficult it is to re-attach them. Therefore, the end face of the second protrusion 366 is closer to the moving scroll 33 axially than the end face of the first protrusion 365. This arrangement can provide support immediately upon the moving scroll 33 detaching from the stationary scroll 32.

[0079] Further, see Figure 4 As shown, in this embodiment, a first annular groove 367 is provided on the side of the first boss 365 near the moving scroll plate 33. The first annular groove 367 is located on the outer periphery of the second bearing hole 362 and is spaced apart from the second bearing hole 362. The first annular groove 367 is arranged around the second bearing hole 362 in the circumferential direction. A sealing element 34 is provided in the first annular groove 367. The sealing element 34 includes an annular sealing ring 341. The first annular groove 367 divides the end face of the first boss 365 near the moving scroll plate 33 into a first end face 3651 and a second end face 3652. The first end face 3651 is closer to the crankshaft 31 than the second end face 3652, and the distance between the first end face 3651 and the moving scroll plate 33 is greater than the distance between the second end face 3652 and the moving scroll plate 33.

[0080] Specifically, since the sealing element 34 in this embodiment is disposed between the moving scroll plate 33 and the bracket 36, an annular groove needs to be opened on the moving scroll plate 33 or the bracket 36 to place the sealing element 34 and form a sealing effect. When the bracket 36 has a first annular groove 367, the first annular groove 367 will divide the end face of the first boss 365 near the moving scroll plate 33 into a first end face 3651 and a second end face 3652. Since the second end face 3652 is closer to the moving scroll plate 33 than the first end face 3651, the height of the outer side wall of the first annular groove 367 away from the second bearing hole 362 is higher than the height of the inner side wall of the first annular groove 367 near the second bearing hole 362. On this basis, under the pressure difference between the first back pressure space 40 and the second back pressure space 50, the sealing element 34 will be expanded so that the sealing element 34 fits against the outer side wall of the first annular groove 367 away from the second bearing hole 362, thereby improving the sealing effect.

[0081] Further, see Figure 5 As shown, in this embodiment, the moving scroll plate 33 is provided with a second annular groove 333 on the side near the bracket 36. The second annular groove 333 is located on the outer periphery of the eccentric bearing hole 332 and is spaced apart from the eccentric bearing hole 332. The second annular groove 333 is arranged around the eccentric bearing hole 332 in the circumferential direction. A sealing element 34 is provided in the second annular groove 333. The sealing element 34 includes an annular sealing ring 341. The second annular groove 333 divides the end face of the moving scroll plate 33 near the bracket 36 into a third end face 334 and a fourth end face 335. The third end face 334 is closer to the crankshaft 31 than the fourth end face 335, and the distance between the third end face 334 and the bracket 36 is greater than the distance between the fourth end face 335 and the bracket 36.

[0082] Specifically, since the sealing element 34 in this embodiment is disposed between the moving scroll plate 33 and the bracket 36, an annular groove needs to be opened on the moving scroll plate 33 or the bracket 36 to place the sealing element 34 and form a sealing effect. When the moving scroll plate 33 has a second annular groove 333, the second annular groove 333 will divide the end face of the moving scroll plate 33 near the bracket 36 into a third end face 334 and a fourth end face 335. Since the fourth end face 335 is closer to the bracket 36 than the third end face 334, the height of the outer wall of the second annular groove 333 away from the eccentric bearing hole 332 will be higher than the height of the inner wall of the second annular groove 333 near the eccentric bearing hole 332. On this basis, under the pressure difference between the first back pressure space 40 and the second back pressure space 50, the sealing element 34 will be expanded so that the sealing element 34 fits against the outer wall of the second annular groove 333 away from the eccentric bearing hole 332, thereby improving the sealing effect.

[0083] Further, see Figure 1As shown, the anti-rotation component 35 in this embodiment 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 component 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.

[0084] As can be seen from the above embodiments, in the compressor of this application, the pump body assembly 30 is placed below the motor 20, and the accommodating cavity 101 is a high-pressure environment. The first bearing portion 322 on the stationary scroll plate 32 and the second bearing portion 361 on the bracket 36 can support the crankshaft 31. There is no need to set a bearing on the other side of the motor 20. Since the pump body assembly 30 in this embodiment is located below the motor 20, the first bearing portion 322 and the second bearing portion 361 are close to the oil storage space 102 at the bottom of the accommodating cavity 101. Therefore, the compressor can operate reliably without additional bushings. Thus, the compressor of this embodiment has the characteristics of simple structure and low cost.

[0085] However, the establishment of back pressure in this structure is more complex. Similar to existing scroll compressors, the compressor in this embodiment also introduces an intermediate pressure between the intake and exhaust pressures into the back pressure chamber to counteract the axial force and torque exerted on the moving scroll 33 by the gas force in the compression chamber 301. However, the difference is that, since the moving scroll 33 in this embodiment is provided with an eccentric bearing hole 332, and the crankshaft 31 is provided with an oil passage to guide lubricating oil into the eccentric bearing hole 332 to lubricate the bearing, after lubricating the eccentric bearing hole 332, the lubricating oil will then flow into the back pressure chamber. At this time, the pressure in the back pressure chamber is determined by the intermediate pressure between the intake and exhaust pressures and the high pressure carried by the lubricating oil. If the lubricating oil is not isolated in a segmented area, the oil pressure influence range will be too large, which will result in an excessively high back pressure. In response to this situation, the solution in this embodiment is to provide a seal 34 between the moving scroll 33 and the bracket 36. The seal 34 is used to isolate the intermediate pressure and the high pressure, so that the intermediate pressure and the high pressure are located in different areas of the back pressure chamber. The high pressure is located on the side of the seal 34 closer to the crankshaft 31, that is, the high pressure is located in the first back pressure space 40, while the intermediate pressure is located in the second back pressure space 50.

[0086] Meanwhile, since the first back pressure space 40 and the second back pressure space 50 are connected by the first channel 60, a throttling effect can be generated when the flow cross-sectional area of ​​the first channel 60 is very small; while the second back pressure space 50 is connected to the compression chamber 301 by the second channel 70, whether the second channel 70 has a throttling effect and the throttling situation can be achieved by controlling the flow cross-sectional area of ​​the second channel 70. In this case, the pressure in the back chamber of the moving scroll plate 33 away from the stationary scroll plate 32 is jointly determined by the pressure of the first pressure space and the pressure of the second pressure space. The first back pressure space 40 is connected to the accommodating chamber 101, and the pressure in the first back pressure space 40 is the high pressure during exhaust; the pressure of the second back pressure space 50 can be adjusted and is controlled by three parts: the flow area of ​​the first channel 60, the flow area of ​​the second channel 70, and the position of the second channel 70.

[0087] The larger the flow cross-sectional area of ​​the first channel 60, the greater the pressure in the second back pressure space 50. Simultaneously, the flow cross-sectional area of ​​the first channel 60 also affects the oil intake of the entire pump assembly 30. If the flow cross-sectional area of ​​the first channel 60 is too large, the oil intake increases, which negatively impacts the compressor's energy efficiency. Conversely, if the flow cross-sectional area of ​​the first channel 60 is too small, the oil intake decreases, resulting in insufficient lubrication of the pump assembly 30. Therefore, the flow cross-sectional area of ​​the first channel 60 is relatively fixed. Meanwhile, the larger the flow area of ​​the second channel 70, the greater the pressure in the second back pressure space 50. The size of the flow area of ​​the second channel 70 affects the lubrication of the lubricating oil in the compression chamber 301. When the flow area of ​​the second channel 70 is too large, the amount of oil entering the compression chamber 301 will increase, thereby affecting the compression effect of the refrigerant and even causing liquid hammer damage to the pump body assembly 30. When the flow area of ​​the second channel 70 is too small, the amount of oil entering the chamber will be less, resulting in poor lubrication effect of the lubricating oil in the compression chamber 301. Therefore, the flow cross-sectional area of ​​the second channel 70 is relatively fixed. Of course, the position of the second channel 70 also affects the pressure of the second back pressure space 50. When the inlet of the second channel 70 is closer to the suction channel 324 on the stationary vortex disk 32 along the first direction, the pressure of the second back pressure space 50 is lower, but at the same time, it may affect the suction process of the suction channel 324. When the inlet of the second channel 70 is farther from the suction channel 324 on the stationary vortex disk 32 along the first direction, the pressure of the second back pressure space 50 is greater, but at the same time, the area of ​​the compression chamber 301 that can be lubricated will be reduced. Therefore, the position of the second channel 70 is relatively fixed. That is to say, when the flow cross-sectional area of ​​the first channel 60, the flow cross-sectional area of ​​the second channel 70, and the position of the second channel 70 are determined, the pressure of the second back pressure space 50 is also determined. At this time, a suitable back pressure can be provided by adjusting the ratio of the area of ​​the first back pressure space 40 and the second back pressure space 50.

[0088] Furthermore, during the compressor startup phase, the pressure in the back pressure chamber is not yet fully established. Under the influence of the gas force in the compression chamber 301, the moving scroll 33 will detach from the stationary scroll 32 along the crankshaft 31 axially. At this time, if the moving scroll 33 is not supported by other components, the axial distance between the moving scroll 33 and the stationary scroll 32 will be too large. This excessive detachment distance will make it more difficult for the moving scroll 33 and the stationary scroll 32 to re-engage. Greater back pressure is required to re-engage them, but greater back pressure will increase operating resistance, increase compressor energy consumption, and reduce compressor performance. Therefore, in this embodiment, a second protrusion 366 is provided on the bracket 36, which can provide support immediately after the moving scroll 33 detaches from the stationary scroll 32.

[0089] 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.

[0090] 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.

[0091] 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.

[0092] 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 used in an air conditioning system, characterized in that, The compressor includes a vertical variable frequency scroll compressor, and the compressor further 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 stationary scroll plate (36). 2) 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 close to the moving scroll plate (33). The moving scroll plate (33) is provided with a second scroll tooth (331) that meshes with the first scroll tooth (321). The first scroll tooth (321) and the second scroll tooth (331) mesh to form a compression cavity (301). The housing (10) is provided with an intake pipe (11) and an exhaust pipe (12). The intake pipe (11) is connected to the pump body assembly (30), and the exhaust pipe (12) is connected to the accommodating cavity (101). The crankshaft (31) includes a first shaft section (311), an eccentric section (312), and a second shaft section (313) arranged sequentially along its own axis. The stationary scroll plate (32) is provided with a first bearing portion (322) on the side away from the moving scroll plate (33). The first bearing portion (322) has a first bearing hole (323). The bracket (36) is provided with a second bearing portion (361) on the side away from the moving scroll plate (33). The second bearing portion (361) has a first bearing hole (323). The moving scroll (33) has a second bearing hole (362), and the moving scroll (33) has an eccentric bearing hole (332). The motor (20) is sleeved on the first shaft section (311) through the rotor (21). The stationary scroll (32) is sleeved on the first shaft section (311) or the second shaft section (313) through the first bearing hole (323). The moving scroll (33) is sleeved on the eccentric section (312) through the eccentric bearing hole (332). The bracket (36) is sleeved on the second shaft section (313) or the first shaft section (311) through the second bearing hole (362). The anti-rotation component (35) is disposed between the moving scroll (33) and the bracket (36). The sealing element (34) is disposed between the moving scroll plate (33) and the bracket (36). The side of the sealing element (34) close to the crankshaft (31) forms a first back pressure space (40) between the moving scroll plate (33) and the bracket (36). The side of the sealing element (34) away from the crankshaft (31) forms a second back pressure space (50) between the moving scroll plate (33), the stationary scroll plate (32), and the bracket (36). The first back pressure space (40) and the second back pressure space (50) are both arranged around the crankshaft (31) circumferentially. The pump body assembly (30) has a first channel (60) and a second channel (70), the first channel (60) being connected to the first back pressure space (40) and the second back pressure space (50), the second channel (70) being connected to the compression chamber (301) and the second back pressure space (50), and the first back pressure space (40) being connected to the receiving chamber (101). Within the projection along the crankshaft (31) axial direction, the projected area of ​​the first back pressure space (40) is S1, and the projected area of ​​the moving scroll plate (33) is S2, wherein S1 and S2 satisfy the relationship: 0.089≤S1 / S2≤0.298; the displacement V of the compressor satisfies the relationship: 6cm 3 ≤V≤10cm 3 The maximum radial dimension D1 of the moving scroll disk (33) along the radial direction of the crankshaft (31) satisfies the following relationship: 76mm≤D1≤84mm.

2. The compressor for use in an air conditioning system according to claim 1, characterized in that, The minimum flow cross-sectional area S3 of the first channel (60) satisfies the following relationship: 0.03 mm 2 ≤S3≤0.12mm 2 The minimum flow cross-sectional area S4 of the second channel (70) satisfies the following relationship: S4 ≥ 0.06 mm 2 .

3. The compressor for use in an air conditioning system according to claim 2, characterized in that, When the minimum flow cross-sectional area S4 of the second channel (70) satisfies the relationship: 0.06mm 2 ≤S4≤0.4mm 2 At that time, the minimum flow cross-sectional area S3 of the first channel (60) satisfies the following relationship: 0.03mm 2 ≤S3≤0.07mm 2 And S1 and S2 satisfy the relationship: 0.133≤S1 / S2≤0.

179.

4. The compressor for use in an air conditioning system according to claim 2, characterized in that, When the minimum flow cross-sectional area S4 of the second channel (70) satisfies the relationship: 0.06mm 2 ≤S4≤0.4mm 2 At that time, the minimum flow cross-sectional area S3 of the first channel (60) satisfies the following relationship: 0.07mm 2 ≤S3≤0.12mm 2 And S1 and S2 satisfy the relationship: 0.089≤S1 / S2≤0.

133.

5. The compressor for use in an air conditioning system according to claim 2, characterized in that, When the minimum flow cross-sectional area S4 of the second channel (70) satisfies the relationship: S4 > 0.4 mm 2 At that time, the minimum flow cross-sectional area S3 of the first channel (60) satisfies the following relationship: 0.07mm 2 ≤S3≤0.12mm 2 And S1 and S2 satisfy the relationship: 0.133≤S1 / S2≤0.

179.

6. The compressor for use in an air conditioning system according to claim 2, characterized in that, When the minimum flow cross-sectional area S4 of the second channel (70) satisfies the relationship: S4 > 0.4 mm 2 At that time, the minimum flow cross-sectional area S3 of the first channel (60) satisfies the following relationship: 0.03mm 2 ≤S3≤0.07mm 2 And S1 and S2 satisfy the relationship: 0.179≤S1 / S2≤0.

298.

7. The compressor for use in an air conditioning system according to any one of claims 1 to 6, characterized in that, The first channel (60) extends radially along the crankshaft (31), and the extension length D2 of the first channel (60) satisfies the relationship: 2mm≤D2≤5mm.

8. The compressor for use in an air conditioning system according to any one of claims 1 to 6, characterized in that, The first vortex tooth (321) is spirally arranged around the outer periphery of the first bearing hole (323), and the static vortex disk (32) is provided with an air intake channel (324), which is connected to the air intake pipe (11); The second channel (70) is disposed on the stationary scroll plate (32). The second channel (70) includes a first flow section (71), a second flow section (72), and a third flow section (73). The first flow section (71) and the third flow section (73) both extend along the axial direction of the crankshaft (31). The second flow section (72) extends from the outer edge of the stationary scroll plate (32) toward the inner side of the stationary scroll plate (32) and communicates with the first flow section (71) and the third flow section (73). The first flow section (71) is closer to the crankshaft (31) than the third flow section (73). The first flow section (71) communicates with the compression chamber (301), and the third flow section (73) communicates with the second back pressure space (50). Starting from the center point O1 of the first bearing hole (323), draw a line O1A connecting it to the central axis of the air intake channel (324), and starting from the center point O1 of the first bearing hole (323), draw a line O1B connecting it to the center of the first flow section (71). Along the spiral winding direction of the first vortex tooth (321), the included angle θ1 between O1A and O1B satisfies the relationship: 240°≤θ1≤320°.

9. The compressor for use in an air conditioning system according to any one of claims 1 to 6, characterized in that, The second spiral tooth (331) is spirally arranged around the outer periphery of the eccentric bearing hole (332); The second channel (70) is disposed on the moving scroll plate (33). The second channel (70) includes a fourth flow section (74) and a fifth flow section. The fourth flow section (74) extends along the axial direction of the crankshaft (31) and communicates with the compression chamber (301). The fifth flow section extends from the outer edge of the moving scroll plate (33) toward the inner side of the moving scroll plate (33) and communicates with the fourth flow section (74) and the second back pressure space (50). Starting from the center point O2 of the eccentric bearing hole (332), draw a line O2C connecting the farthest point of the second vortex tooth (331) along the radial direction of the crankshaft (31). Starting from the center point O2 of the eccentric bearing hole (332), draw a line O2D connecting the center of the fourth flow section (74). Along the spiral winding direction of the second vortex tooth (331), the included angle θ2 between O2C and O2D satisfies the relationship: 250°≤θ2≤330°.

10. A compressor for use in an air conditioning system according to any one of claims 1 to 6, characterized in that, The stationary scroll plate (32) has a first plane (325) on the side near the moving scroll plate (33), and the support (36) has a second plane (363) on the side near the moving scroll plate (33). A receiving groove (364) is provided on the second plane (363). A first boss (365) and a second boss (366) are provided in the receiving groove (364). The first boss (365) and the second boss (366) are arranged around the circumference of the support (36) and are arranged in sequence from the inside to the outside along the radial direction of the crankshaft (31). Along the axial direction of the crankshaft (31), the distance between the first boss (365) and the second plane (363) is greater than the distance between the second boss (366) and the second plane (363). The second bearing hole (362) passes through the first boss (365), the seal (34) is located between the moving scroll (33) and the first boss (365), and the first plane (325) is in contact with the second plane (363). When the moving scroll (33) moves axially along the crankshaft (31) toward a direction away from the stationary scroll (32), the end face of the second boss (366) near the moving scroll (33) is in contact with the side of the moving scroll (33) away from the stationary scroll (32).

11. The compressor for use in an air conditioning system according to claim 10, characterized in that, The first boss (365) is provided with a first annular groove (367) on the side near the moving scroll plate (33). The first annular groove (367) is located on the outer periphery of the second bearing hole (362) and is spaced apart from the second bearing hole (362). The first annular groove (367) is arranged around the second bearing hole (362) in the circumferential direction. The sealing member (34) is provided in the first annular groove (367). The sealing member (34) includes an annular sealing ring (341). The first annular groove (367) divides the end face of the first boss (365) near the moving scroll disk (33) into a first end face (3651) and a second end face (3652). The first end face (3651) is closer to the crankshaft (31) than the second end face (3652), and the distance between the first end face (3651) and the moving scroll disk (33) is greater than the distance between the second end face (3652) and the moving scroll disk (33).

12. The compressor for use in an air conditioning system according to claim 10, characterized in that, The moving scroll plate (33) is provided with a second annular groove (333) on the side near the bracket (36). The second annular groove (333) is located on the outer periphery of the eccentric bearing hole (332) and is spaced apart from the eccentric bearing hole (332). The second annular groove (333) is arranged around the eccentric bearing hole (332) in a circumferential direction. The sealing element (34) is provided in the second annular groove (333). The sealing element (34) includes an annular sealing ring (341). The second annular groove (333) divides the end face of the moving scroll disk (33) near the bracket (36) into a third end face (334) and a fourth end face (335). The third end face (334) is closer to the crankshaft (31) than the fourth end face (335), and the distance between the third end face (334) and the bracket (36) is greater than the distance between the fourth end face (335) and the bracket (36).

13. 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 12.

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