Compressor applied to air conditioning system and air conditioning system

Abstract

This application discloses a compressor and an air conditioning system for use in an air conditioning system. The compressor further includes a housing, a motor, and a pump assembly. The pump assembly includes a crankshaft, a stationary scroll, a moving scroll, an anti-rotation component, and a frame. The stationary scroll has a first scroll tooth portion, and the moving scroll has a second scroll tooth portion. The first and second scroll tooth portions mesh to form a compression chamber. The stationary scroll has a first plane, and the frame has a second plane. The second plane is attached to the first plane, and a receiving groove is formed on the second plane. A sealing boss and a supporting boss are provided in the receiving groove. The sealing boss and the supporting boss are coaxially arranged and spaced apart radially along the crankshaft. Axially along the crankshaft, the distance between the sealing boss and the end face of the moving scroll near the frame is greater than the distance between the supporting boss and the end face of the moving scroll near the frame. This application can solve the problems of low reliability and low energy efficiency of existing scroll compressors.

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] In a scroll compressor operating under high pressure, a back pressure environment is required on the back of the scroll (the side opposite to the scroll) to ensure the moving disc remains in close contact with the stationary disc. Excessive or insufficient pressure within this back pressure environment can negatively impact the scroll compressor. Furthermore, since the moving disc is driven by the crankshaft, the center of the moving disc is also under high pressure when the crankshaft is in a high-pressure environment. Therefore, it is necessary to separate the back pressure environment from the high-pressure environment on the back of the moving disc. Current technology achieves this separation by providing a sealing plane on the frame opposite the back of the moving disc and by establishing a sealing structure between the frame and the back of the moving disc.

[0003] At the same time, since the moving plate is a moving part, there is an axial gap between the moving plate and the stationary plate and the frame. This gap is called the floating amount. If the floating amount is too large or too small, it will have an adverse effect on the moving plate. The floating amount is determined by the position of the moving plate support surface set on the frame. In the prior art, the moving plate support surface and the sealing plane on the frame are the same surface.

[0004] However, when the sealing plane and the moving plate support surface are on the same plane, two adverse consequences arise. First, to support the moving plate, the sealing plane needs to be larger, increasing the cost of the sealing structure. Second, because the inner side of the sealing plane is under high pressure and the outer side is under back pressure, a pressure difference exists between the two sides. This pressure difference causes hard particles to pass through the sealing plane. When the float is small, these hard particles accumulate between the sealing plane and the moving plate, causing wear on the moving plate and ultimately affecting the compressor's operational reliability. Summary of the Invention

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

[0006] According to one aspect of this application, a compressor for use in an air conditioning system is provided, the compressor comprising a vertical variable frequency scroll compressor, the compressor further comprising:

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

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

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

[0010] The housing is provided with an intake pipe and an exhaust pipe. The intake pipe is connected to the compression chamber, and the exhaust pipe is connected to the accommodating chamber. The crankshaft includes a first shaft section, an eccentric section, and a second shaft section. The first shaft section is located on the side of the eccentric section closer to the motor, and the second shaft section is located on the side of the eccentric section away from the motor. A first bearing portion with a first bearing hole is provided on the side of the stationary scroll plate away from the moving scroll plate. A second bearing portion with a second bearing hole is provided on the side of the frame away from the moving scroll plate. The moving scroll plate has an eccentric bearing hole. The motor is driven and connected to the crankshaft. The stationary scroll plate is sleeved on the first shaft section or the second shaft section through the first bearing hole. The moving scroll plate is sleeved on the eccentric section through the eccentric bearing hole. The frame is sleeved on the second shaft section or the first shaft section through the second bearing hole. An anti-rotation component is provided between the moving scroll plate and the frame.

[0011] The stationary scroll plate has a first plane on the side near the moving scroll plate, and the frame has a second plane on the side near the moving scroll plate. The second plane fits into the first plane. A receiving groove is formed on the second plane. A sealing boss and a supporting boss are provided in the receiving groove. Both the sealing boss and the supporting boss protrude from the bottom of the receiving groove and are coaxially arranged and spaced apart from the inside to the outside along the radial direction of the crankshaft. The sealing element is located between the sealing boss and the moving scroll plate. The second bearing hole passes through the sealing boss. Along the axial direction of the crankshaft, the distance between the sealing boss and the end face of the moving scroll plate near the frame is greater than the distance between the supporting boss and the end face of the moving scroll plate near the frame.

[0012] Furthermore, along the radial direction of the crankshaft, the minimum distance D1 between the support boss and the center of the second bearing hole satisfies the relationship: D1≥30mm.

[0013] Furthermore, the moving scroll disk includes a moving disk base plate, and the second scroll tooth portion is disposed on the side of the moving disk base plate near the stationary scroll disk;

[0014] Along the axial direction of the crankshaft, the minimum distance between the support boss and the second plane is H1, and the thickness of the moving disk substrate is T1, wherein H1 and T1 satisfy the relationship: 0.01mm≤H1-T1≤0.025mm.

[0015] Furthermore, along the axial direction of the crankshaft, the distance between the sealing boss and the bottom of the receiving groove is H2, and the distance between the supporting boss and the bottom of the receiving groove is H3, wherein H2 and H3 satisfy the relationship: 0.05mm≤H3-H2≤0.5mm.

[0016] Furthermore, the support boss is arranged circumferentially around the second bearing hole in the receiving groove, and the support boss is provided with a plurality of grooves, which are spaced apart circumferentially along the support boss to divide the support boss into a plurality of support segments.

[0017] Furthermore, each of the support segments has a first end and a second end. The line connecting the end of each first end to the center of the second bearing hole is a first straight line, and the line connecting the end of each second end to the center of the second bearing hole is a second straight line. An angle is formed between each first straight line and each second straight line, and the sum of the angles is greater than or equal to 180°.

[0018] Furthermore, within the projection along the crankshaft axis, the sum of the projected areas of each of the support segments is greater than and equal to 300 mm². 2 .

[0019] Furthermore, along the radial direction of the crankshaft, the minimum distance between the support boss and the center of the second bearing hole is L, the eccentricity of the eccentric section is e, and the maximum radial dimension of the moving scroll disk is P, wherein L, e, and P satisfy the relationship: P / 2-Le≥1.5mm.

[0020] Furthermore, when the crankshaft drives the moving scroll disk to rotate and translate, the minimum distance D2 between the outer edge of the moving scroll disk and the second plane along the radial direction of the crankshaft satisfies the relationship: D2≥0.2mm.

[0021] Furthermore, the support boss is circumferentially arranged in the receiving groove along the second bearing hole, and a first annular groove is provided between the support boss and the side wall of the receiving groove. The first annular groove is circumferentially arranged along the support boss and radially along the crankshaft. The minimum width D3 of the first annular groove satisfies the relationship: D3≥1mm.

[0022] Furthermore, along the axial direction of the crankshaft, the distance H4 between the end face of the support boss near the moving scroll disk and the bottom of the first annular groove satisfies the following relationship: H4≥0.2mm.

[0023] Furthermore, the moving scroll disk includes a moving disk base plate, the second scroll tooth portion is disposed on the side of the moving disk base plate near the stationary scroll disk, the moving disk base plate is provided with a second annular groove, the second annular groove is disposed around the outer peripheral side of the moving disk base plate along the circumference of the crankshaft, and the cross-sectional area S of the second annular groove satisfies the relationship: S≥1mm 2 .

[0024] Furthermore, the first plane and the second plane that are fitted together have an overlapping sealing surface, and the minimum width D4 of the overlapping sealing surface along the radial direction of the crankshaft satisfies the relationship: D4≥2mm.

[0025] Furthermore, a third annular groove is provided on the sealing boss. The third annular groove is arranged around the end face of the sealing boss near the moving scroll plate along the circumference of the second bearing hole. The sealing element is provided in the third annular groove. The side of the sealing element near the crankshaft, together with the moving scroll plate and the frame, forms a first pressure space. The side of the sealing element away from the crankshaft, together with the stationary scroll plate, the moving scroll plate and the frame, forms a second pressure space. The pressure in the first pressure space is greater than the pressure in the second pressure space. The first pressure space is connected to the oil storage space.

[0026] The stationary vortex disk is provided with a medium-pressure channel, which connects the compression chamber and the second pressure space.

[0027] Furthermore, the third annular groove divides the sealing boss into a first boss and a second boss. The first boss is closer to the second bearing hole than the second boss. Along the axial direction of the crankshaft, the distance H5 between the first boss and the bottom of the receiving groove is less than the distance H6 between the second boss and the bottom of the receiving groove. The distance H7 between the first boss and the extended surface of the end face of the supporting boss near the moving scroll plate satisfies the relationship: 0.5mm≤H7≤1mm.

[0028] Furthermore, the rated cooling capacity Q of the air conditioning system satisfies the following relationship: 2500W≤Q≤3700W.

[0029] Furthermore, along the radial direction of the crankshaft, the maximum radial dimension D5 of the stator satisfies the relationship: 96mm ≤ D5 ≤ 104mm; and / or,

[0030] Along the radial direction of the crankshaft, the maximum radial dimension D6 of the moving scroll disk satisfies the relationship: 78mm≤D6≤82mm.

[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] In this application, the moving scroll is easily affected by the gas force in the compression chamber and moves away from the stationary scroll, resulting in gas leakage in the compression chamber. To address this, this application makes the distance between the sealing boss and the end face of the moving scroll near the frame greater than the distance between the support boss and the end face of the moving scroll near the frame. That is, the support boss is closer to the moving scroll than the sealing boss. Thus, as the moving scroll moves away from the stationary scroll, the support boss can provide support for the moving scroll. Furthermore, since the support boss is farther from the second bearing hole than the sealing boss, the part of the support boss that supports the moving scroll is farther from the center of the eccentric bearing hole, thereby providing more stable support for the moving scroll. This makes it easier for the moving scroll to transition from a state of not being in contact with the stationary scroll to a state of being in contact with the stationary scroll. At this time, the side of the moving scroll near the frame does not require much back pressure to support the moving scroll, effectively improving the energy efficiency of the compressor.

[0033] Meanwhile, since the sealing boss in this application does not support the moving scroll and is axially far from it, it is less likely for hard, small particles of impurities to accumulate at the sealing boss on the frame, effectively preventing wear on the moving scroll and improving the compressor's reliability. Furthermore, because the second bearing hole in this application penetrates the sealing boss, meaning the sealing boss is closer to the frame center, the material used in the sealing structure can be reduced, improving the compressor's cost-effectiveness. In addition, since the support boss in this application does not perform a sealing function, it is not affected by pressure differential. Even with small fluctuations, hard, small particles of impurities have no power to enter the support boss and cause wear. Attached Figure Description

[0034] 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:

[0035] Figure 1 This is a cross-sectional view of the compressor disclosed in an embodiment of this application;

[0036] Figure 2 This is a cross-sectional view of the moving scroll plate and frame disclosed in the embodiments of this application;

[0037] Figure 3 This is a schematic diagram of the structure of the moving vortex disk disclosed in the embodiments of this application;

[0038] Figure 4 This is a cross-sectional view of the moving scroll disk disclosed in the embodiments of this application;

[0039] Figure 5 This is a schematic diagram of the static vortex disk disclosed in the embodiments of this application from a first-view perspective;

[0040] Figure 6 This is a schematic diagram of the static vortex disk disclosed in the embodiments of this application from a second perspective.

[0041] Figure 7 This is a cross-sectional view of the stationary vortex disk disclosed in the embodiments of this application;

[0042] Figure 8 This is a cross-sectional view of the crankshaft disclosed in an embodiment of this application;

[0043] Figure 9 This is a schematic diagram of the rack structure disclosed in the embodiments of this application;

[0044] Figure 10 This is a cross-sectional view of the rack disclosed in an embodiment of this application;

[0045] Figure 11 This is a schematic diagram of the structure of the frame (with grooves) disclosed in the embodiments of this application;

[0046] Figure 12 This is a top view of the frame (with grooves) disclosed in an embodiment of this application;

[0047] Figure 13 This is a schematic diagram of the structure of the frame (with a first annular groove) disclosed in the embodiments of this application;

[0048] Figure 14 The appendices disclosed in the embodiments of this application Figure 13 AA section view in the image.

[0049] The above figures include the following reference numerals:

[0050] 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 bore; 324. First plane; 325. Intermediate pressure channel; 326. Intake port; 327. Exhaust port; 33. Moving scroll plate; 331. Second scroll tooth section; 332. Eccentric bearing 333. Hole; 34. Seal; 35. Anti-rotation component; 36. Frame; 361. Second bearing section; 362. Second bearing hole; 363. Second plane; 364. Receiving groove; 365. Sealing boss; 3651. First boss; 3652. Second boss; 366. Support boss; 37. Support section; 371. First straight line; 372. Second straight line; 40. Groove; 41. First annular groove; 42. Second annular groove; 43. Third annular groove; 44. Overlapping sealing surface; 50. First pressure space; 60. Second pressure space; 70. Liquid reservoir. Detailed Implementation

[0051] 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.

[0052] 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.

[0053] 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.

[0054] See Figures 1 to 14 As shown, according to an embodiment of this application, a compressor for use in an air conditioning system is provided. The compressor includes a vertical variable frequency scroll compressor, and the compressor also includes a housing 10, a motor 20, and a pump assembly 30.

[0055] 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. The pump body assembly 30 includes a crankshaft 31, a stationary scroll 32, a moving scroll 33, a seal 34, an anti-rotation component 35, and a frame 36. The crankshaft 31 is rotatably disposed in the receiving cavity 101. The stationary scroll 32 is provided with a first scroll tooth 321 on the side near the moving scroll 33. The moving scroll 33 is provided with a second scroll tooth 331 that meshes with the first scroll tooth 321. The first scroll tooth 321 and the second scroll tooth 331 mesh to form a compression cavity 301.

[0056] The housing 10 is equipped with an intake pipe 11 and an exhaust pipe 12. The intake pipe 11 is connected to the compression chamber 301, and the exhaust pipe 12 is connected to the accommodating chamber 101. The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. 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. A first bearing portion 322 is provided on the side of the stationary scroll plate 32 away from the moving scroll plate 33. The 322 has a first bearing hole 323. A second bearing section 361 is provided on the side of the frame 36 opposite to the moving scroll 33. The second bearing section 361 has a second bearing hole 362. The moving scroll 33 has an eccentric bearing hole 332. The motor 20 is driven by the crankshaft 31. The stationary scroll 32 is fitted onto the first shaft section 311 or the second shaft section 313 through the first bearing hole 323. The moving scroll 33 is fitted onto the eccentric section 312 through the eccentric bearing hole 332. The frame 36 is fitted onto the second bearing hole 362. The second shaft segment 313 or the first shaft segment 311, with the anti-rotation component 35 disposed between the moving scroll plate 33 and the frame 36; the stationary scroll plate 32 has a first plane 324 on the side near the moving scroll plate 33, and the frame 36 has a second plane 363 on the side near the moving scroll plate 33, the second plane 363 fitting against the first plane 324, and a receiving groove 364 formed on the second plane 363, with a sealing boss 365 and a supporting boss 366 disposed within the receiving groove 364, the sealing boss 365 and the supporting boss 366... All 6 protrude from the bottom of the receiving groove 364, and the sealing boss 365 and the supporting boss 366 are coaxially arranged and arranged in sequence from the inside to the outside along the radial direction of the crankshaft 31. The sealing element 34 is located between the sealing boss 365 and the moving scroll 33. The second bearing hole 362 passes through the sealing boss 365. Along the axial direction of the crankshaft 31, the distance between the sealing boss 365 and the end face of the moving scroll 33 near the frame 36 is greater than the distance between the supporting boss 366 and the end face of the moving scroll 33 near the frame 36.

[0057] It is understood that in this embodiment, the stationary scroll 32 may be fitted onto the first shaft segment 311 through the first bearing hole 323, and the frame 36 may be fitted onto the second shaft segment 313 through the second bearing hole 362; alternatively, the stationary scroll 32 may be fitted onto the second shaft segment 313 through the first bearing hole 323, and the frame 36 may be fitted onto the first shaft segment 311 through the second bearing hole 362. (The appendix of this embodiment is missing.) Figure 1 The diagram shows the case where the stationary vortex disk 32 is fitted onto the first shaft section 311 through the first bearing hole 323, and the frame 36 is fitted onto the second shaft section 313 through the second bearing hole 362.

[0058] 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 away 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. This compresses the refrigerant that enters the compression chamber 301 through the intake pipe 11. Subsequently, the compressed refrigerant is discharged into the accommodating cavity 101 and then discharged to the outside of the compressor through the exhaust pipe 12 connected to the accommodating cavity 101.

[0059] During the compression process described above, the moving scroll plate 33 is easily affected by the gas force within the compression chamber 301 and moves away from the stationary scroll plate 32, resulting in gas leakage within the compression chamber 301. Therefore, in this embodiment, the distance between the sealing boss 365 and the end face of the moving scroll plate 33 near the frame 36 is made greater than the distance between the supporting boss 366 and the end face of the moving scroll plate 33 near the frame 36. That is, the supporting boss 366 is closer to the moving scroll plate 33 than the sealing boss 365. Thus, as the moving scroll plate 33 moves away from the stationary scroll plate 32, the supporting boss... The boss 366 provides support for the moving scroll 33. Since the supporting boss 366 is farther from the second bearing hole 362 than the sealing boss 365, the part of the supporting boss 366 that supports the moving scroll 33 is far from the center of the eccentric bearing hole 332. This allows for more stable support of the moving scroll 33, making it easier for the moving scroll 33 to transition from a state of not being in contact with the stationary scroll 32 to a state of being in contact with the stationary scroll 32. At this time, the side of the moving scroll 33 closest to the frame 36 does not require much back pressure to support the moving scroll 33, effectively improving the energy efficiency of the compressor.

[0060] Meanwhile, since the sealing boss 365 in this embodiment does not support the moving scroll 33 and is axially far from it, it is less likely for hard, small particles of impurities to accumulate at the sealing boss 365 on the frame 36. This effectively prevents impurities from causing wear on the moving scroll 33 and improves the reliability of the compressor. Furthermore, since the second bearing hole 362 in this embodiment penetrates the sealing boss 365, meaning the sealing boss 365 is closer to the center of the frame 36, the material used in the sealing structure can be reduced, improving the compressor's cost-effectiveness. In addition, since the support boss 366 in this embodiment does not perform a sealing function, it is not affected by pressure differential. Even with a small fluctuation, hard, small particles of impurities have no power to enter the support boss 366 and cause wear.

[0061] Furthermore, since the stationary scroll plate 32 in this embodiment has a first bearing portion 322 and the frame 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. Simultaneously, 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.

[0062] Specifically, 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.

[0063] Furthermore, along the radial direction of the crankshaft 31, the minimum distance D1 between the center of the support boss 366 and the center of the second bearing hole 362 in this embodiment (e.g., ...) Figure 10 As shown, the relationship must be satisfied: D1 ≥ 30mm. For example, D1 can be set to 30mm, 31mm, 32mm, 33mm, 34mm, 35mm, 36mm, 37mm, 38mm, 39mm, 40mm, etc. In this way, better support can be provided for the part of the moving scroll plate 33 that is far away from the eccentric bearing hole 332, so that the moving scroll plate 33 can be supported more stably, and it is easier for the moving scroll plate 33 to change from a state of not being in contact with the stationary scroll plate 32 to a state of being in contact with the stationary scroll plate 32.

[0064] Further, see Figure 2 As shown, in this embodiment, the moving scroll disk 33 includes a moving disk base plate 333, and a second scroll tooth portion 331 is disposed on the side of the moving disk base plate 333 near the stationary scroll disk 32; along the axial direction of the crankshaft 31, the minimum distance between the support boss 366 and the second plane 363 is H1 (e.g., Figure 2 As shown), the thickness of the moving disk substrate 333 is T1 (as shown). Figure 2 As shown in the figure, H1 and T1 satisfy the following relationship: 0.01mm≤H1-T1≤0.025mm. For example, H1-T1 can be set to 0.01mm, 0.02mm, 0.04mm, 0.06mm, 0.08mm, 0.1mm, 0.12mm, 0.14mm, 0.16mm, 0.18mm, 0.2mm, 0.22mm, 0.24mm, 0.25mm, etc.

[0065] Specifically, the minimum distance H1 between the supporting boss 366 and the second plane 363 minus the thickness T1 of the moving plate base 333 is the floating clearance of the moving scroll 33. When H1-T1 is greater than 0.025mm, the floating clearance of the moving scroll 33 is too large, which can easily lead to a higher back pressure environment and reduce the energy efficiency of the compressor. When H1-T1 is less than 0.01mm, the floating clearance of the moving scroll 33 is too small, which can easily cause the moving scroll 33 to deform due to pressure and temperature, resulting in abnormal contact friction, which in turn affects the reliability and energy efficiency of the compressor, and makes the machining precision of the moving scroll 33 more stringent. That is to say, in this embodiment, by ensuring that H1 and T1 satisfy the relationship: 0.01mm≤H1-T1≤0.025mm, the reliability of the compressor can be effectively guaranteed, and the energy efficiency of the compressor can be kept at a high level.

[0066] Further, see Figure 10 As shown, in this embodiment, along the axial direction of the crankshaft 31, the distance between the sealing boss 365 and the bottom of the receiving groove 364 is H2 (e.g., Figure 10 As shown), the distance between the support boss 366 and the bottom of the receiving groove 364 is H3 (as shown). Figure 10 As shown in the figure, H2 and H3 satisfy the relationship: 0.05mm≤H3-H2≤0.5mm. For example, H3-H2 can be set to 0.05mm, 0.1mm, 0.15mm, 0.2mm, 0.25mm, 0.3mm, 0.35mm, 0.4mm, 0.45mm, 0.5mm, etc.

[0067] Specifically, due to the higher temperature and pressure at the center of the moving scroll plate 33, the deformation at the center of the moving scroll plate 33 will be greater. To ensure that the moving scroll plate 33 contacts the support boss 366 first when moving away from the stationary scroll plate 32, a certain height difference must be maintained between the support boss 366 and the sealing boss 365. When H3-H2 is greater than 0.5mm, the sealing boss 365 is too far from the back of the moving scroll plate 33, and the seal 34 cannot achieve a sealing effect. It is worth noting that the seal 34 in this embodiment uses a rectangular sealing ring as the sealing structure. The rectangular sealing ring will be subjected to radial compression by the pressure difference. Therefore, the height difference between the support platform and the sealing platform cannot be too large, otherwise the pressure-bearing surface of the rectangular sealing ring will be too small, and the outer periphery of the rectangular sealing ring will be deformed and worn. Therefore, in this embodiment, the support boss 366 is axially higher than the sealing boss 365 by 0.05mm to 0.5mm, which increases the pressure-bearing surface of the rectangular sealing ring and effectively prevents the outer periphery of the rectangular sealing ring from being worn.

[0068] Further, see Figures 11 to 12As shown, in this embodiment, the support boss 366 is circumferentially arranged within the receiving groove 364 along the second bearing hole 362. The support boss 366 has multiple grooves 40 spaced apart circumferentially to divide it into multiple support segments 37. This arrangement ensures that when hard, small particulate impurities are present on the support boss 366, these impurities can be promptly removed from the support segment 37 and transferred to the grooves 40, thus guaranteeing the reliability of the support segment 37.

[0069] Further, see Figure 12 As shown, each support segment 37 in this embodiment has a first end and a second end. The line connecting the end of each first end to the center of the second bearing hole 362 is a first straight line 371, and the line connecting the end of each second end to the center of the second bearing hole 362 is a second straight line 372. An angle is formed between each first straight line 371 and each second straight line 372, and the sum of these angles is greater than or equal to 180°, such as 180°, 190°, 200°, 210°, 220°, 230°, 240°, 250°, etc. This configuration ensures that during the rotational translation of the moving scroll plate 33, the support segment 37 has a large support range in the circumferential direction of the moving scroll plate 33, thereby improving the overturning of the moving scroll plate 33 and effectively improving the reliability and energy efficiency of the compressor.

[0070] It is understood that the support segment 37 in this embodiment includes two, three, or more segments. Figure 12 The diagram illustrates the case where there are four support segments 37, and the angles formed by the four support segments 37 and the center of the second bearing hole 362 are θ1, θ2, θ3, and θ4, respectively, where θ1 + θ2 + θ3 + θ4 ≥ 180°. Similarly, when there are two support segments 37, the angles formed by the two support segments 37 and the center of the second bearing hole 362 are θ1 and θ2, respectively, where θ1 + θ2 ≥ 180°; when there are three support segments 37, the angles formed by the three support segments 37 and the center of the second bearing hole 362 are θ1, θ2, and θ3, respectively, where θ1 + θ2 + θ3 ≥ 180°. This process continues for any number of support segments 37 other than those described above.

[0071] Further, see Figure 12 As shown, within the projection along the crankshaft 31 axial direction, the sum of the projected areas of each support segment 37 in this embodiment is greater than and equal to 300 mm². 2 For example, 300mm 2 310mm 2 320mm 2 330mm 2 340mm 2 350mm 2 360mm 2370mm 2 380mm 2 390mm 2 400mm 2 Etc. The appendix of this embodiment Figure 12 The shaded areas represent the projected areas of each support segment 37.

[0072] Specifically, since the back pressure on the back of the moving scroll 33 builds up more slowly than the pressure in the compression chamber 301 when the compressor starts up, the downward force exerted by the compression chamber 301 on the moving scroll 33 is relatively large when the compressor starts up and the back pressure has not yet fully built up. This downward force acts on the support boss 366. Therefore, the support section 37 needs to have a certain area. In this embodiment, the sum of the projected areas of each support section 37 is greater than or equal to 300 mm². 2 This effectively ensures the supporting effect of the support section 37 on the moving scroll disk 33. It can be understood that the sum of the projected areas of each support section 37 in this embodiment is S1+S2+S3+S4.

[0073] Furthermore, along the radial direction of the crankshaft 31, the minimum distance between the support boss 366 and the center of the second bearing hole 362 in this embodiment is L (e.g., Figure 10 As shown), the eccentricity of eccentric segment 312 is e (as shown). Figure 8 As shown), the maximum radial dimension of the moving scroll disk 33 is P (as shown). Figure 4 As shown in the figure, L, e, and P satisfy the relationship: P / 2-Le ≥ 1.5mm, for example, 1.5mm, 1.6mm, 1.7mm, 1.8mm, 1.9mm, 2mm, 2.1mm, 2.2mm, 2.3mm, etc. This setting ensures the minimum support width between the back of the moving scroll plate 33 and the support boss 366. When P / 2-Le is less than 1.5mm, the support width is too small, resulting in a large surface pressure on the support boss 366, which in turn reduces the reliability of the support boss 366.

[0074] Furthermore, in this embodiment, when the crankshaft 31 drives the moving scroll disk 33 to rotate and translate, the minimum distance D2 between the outer edge of the moving scroll disk 33 and the second plane 363 along the radial direction of the crankshaft 31 is (e.g., ...). Figure 2 As shown, the following relationship is satisfied: D2≥0.2mm. For example, D2 can be set to 0.2mm, 0.3mm, 0.4mm, 0.5mm, 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1mm, etc.

[0075] Specifically, since the back pressure chamber is filled with an oil-gas mixture, the rotating scroll 33 will drive and compress the oil-gas mixture within it during its translational motion. Therefore, a certain gap needs to be maintained between the outer edge of the rotating scroll 33 and the second plane 363 to allow the oil-gas mixture to flow, reducing the resistance caused by the compression and thus improving the compressor's efficiency. When D2 is less than 0.2mm, the gap between the outer edge of the rotating scroll 33 and the second plane 363 is too small, making it difficult for the oil-gas mixture to flow through, resulting in increased resistance. It should be noted that in this embodiment, the back pressure chamber refers to the chamber on the side of the rotating scroll 33 furthest from the stationary scroll 32.

[0076] Further, see Figures 13 to 14 As shown, in this embodiment, the support boss 366 is circumferentially arranged around the second bearing hole 362 within the receiving groove 364. A first annular groove 41 is provided between the support boss 366 and the side wall of the receiving groove 364. The first annular groove 41 is circumferentially arranged around the support boss 366, and along the radial direction of the crankshaft 31, the minimum width D3 of the first annular groove 41 (e.g., Figure 14 As shown, the following relationship is satisfied: D3≥1mm. For example, D3 can be set to 1mm, 1.2mm, 1.4mm, 1.6mm, 1.8mm, 2mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, 3mm, etc.

[0077] Specifically, since the back pressure chamber is filled with an oil-gas mixture, the rotating scroll 33 will drive and compress the oil-gas mixture in the back pressure chamber. Therefore, a certain gap needs to be maintained between the support boss 366 and the side wall of the receiving groove 364 to allow the oil-gas mixture to flow. In this embodiment, a first annular groove 41 is provided between the support boss 366 and the side wall of the receiving groove 364, and the width of the first annular groove 41 along the radial direction of the crankshaft 31 is greater than or equal to 1 mm. This reduces the resistance of the oil-gas mixture to the rotating scroll 33 due to compression, thereby improving the compressor's energy efficiency. In addition, the provision of the first annular groove 41 facilitates the machining of the support boss 366. When D3 is less than 1 mm, the radial width of the first annular groove 41 is too small, making it difficult for the oil-gas mixture to flow through the gap, thereby increasing the resistance of the oil-gas mixture to the rotating scroll 33 and reducing the compressor's energy efficiency.

[0078] Furthermore, along the axial direction of the crankshaft 31, the distance H4 between the end face of the support boss 366 near the moving scroll disk 33 and the bottom of the first annular groove 41 in this embodiment (e.g., ...) Figure 14As shown, the following relationship is satisfied: H4 ≥ 0.2 mm. For example, H4 can be set to 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.

[0079] Specifically, since the support boss 366 in this embodiment plays the role of supporting the moving scroll disk 33, when H4 is greater than or equal to 0.2mm, a more stable support structure can be formed between the support boss 366 and the first annular groove 41. Thus, when the moving scroll disk 33 overturns, it can better withstand the overturning force of the moving scroll disk 33 moving away from the stationary scroll disk 32, and can provide support for the moving scroll disk 33, so that the moving scroll disk 33 changes from a state of not being in contact with the stationary scroll disk 32 to a state of being in contact with the stationary scroll disk 32.

[0080] Further, see Figures 3 to 4 As shown, the moving scroll plate 33 in this embodiment includes a moving plate base plate 333, a second scroll tooth portion 331 is disposed on the side of the moving plate base plate 333 near the stationary scroll plate 32, a second annular groove 42 is provided on the moving plate base plate 333, the second annular groove 42 is disposed around the outer peripheral side of the moving plate base plate 333 along the circumference of the crankshaft 31, and the cross-sectional area S of the second annular groove 42 satisfies the relationship: S≥1mm 2 For example, S can be set to 1mm. 2 1.2mm 2 1.4mm 2 1.6mm 2 1.8mm 2 2mm 2 2.2mm 2 2.4mm 2 2.6mm 2 2.8mm 2 3mm 2 It should be noted that, in this embodiment, "the cross-sectional area of ​​the second annular groove 42" refers to the area of ​​the cross section obtained by cutting the second annular groove 42 along the axial direction of the crankshaft 31.

[0081] Specifically, since the back pressure chamber is filled with an oil-gas mixture, the rotating scroll plate 33 will drive and compress the oil-gas mixture in the back pressure chamber during its rotational translation. Therefore, in this embodiment, a second annular groove 42 is provided around the outer periphery of the rotating plate base plate 333. This second annular groove 42 facilitates the flow of the oil-gas mixture, reduces the resistance to the rotating scroll plate 33 caused by the compression of the oil-gas mixture, and effectively improves the compressor's energy efficiency. When S is less than 1mm... 2When the cross-sectional area of ​​the second annular groove 42 is small, the oil-gas mixture is difficult to flow through the second annular groove 42, thereby increasing the resistance of the oil-gas mixture to the moving scroll plate 33 and reducing the energy efficiency of the compressor.

[0082] Further, see Figures 1 to 2 As shown, in this embodiment, the first plane 324 and the second plane 363 that are fitted together have an overlapping sealing surface 44. Along the radial direction of the crankshaft 31, the minimum width D4 of the overlapping sealing surface 44 (e.g., Figure 1 As shown, the following relationship is satisfied: D4≥2mm. For example, D4 ​​can be set to 2mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, 3mm, 3.2mm, 3.4mm, 3.6mm, 3.8mm, 4mm, etc.

[0083] Specifically, when the first plane 324 and the second plane 363 are in contact, they form an overlapping sealing surface 44. The pressure in the space inside the overlapping sealing surface 44 (i.e., the space on the side of the overlapping sealing surface 44 closer to the crankshaft 31) is an intermediate pressure, while the pressure in the space outside the overlapping sealing surface 44 (i.e., the accommodating cavity 101) is a high pressure formed by the exhaust pressure. A significant pressure difference exists between the two sides. If the high-pressure refrigerant on the outside leaks into the intermediate pressure space, it will cause excessive back pressure, affecting oil lubrication. Furthermore, excessive back pressure will cause excessive adhesion between the moving scroll 33 and the stationary scroll 32, leading to excessive friction and severe wear on both, reducing the compressor's reliability and energy efficiency. To ensure that the high-pressure refrigerant on the outside does not leak into the intermediate pressure space, the width of the overlapping sealing surface 44 needs to be ensured; the greater the width, the better the sealing effect. When D4 is less than 2mm, the width of the overlapping sealing surface 44 is too small, which reduces the sealing effect of the overlapping sealing surface 44 and makes it difficult to prevent the high pressure in the accommodating cavity 101 from entering the back pressure cavity.

[0084] Further, see Figures 13 to 14 As shown, in this embodiment, a third annular groove 43 is provided on the sealing boss 365. The third annular groove 43 is arranged around the end face of the sealing boss 365 near the moving scroll plate 33 along the circumference of the second bearing hole 362. A sealing element 34 is provided in the third annular groove 43. The side of the sealing element 34 near the crankshaft 31, together with the moving scroll plate 33 and the frame 36, forms a first pressure space 50. The side of the sealing element 34 away from the crankshaft 31, together with the stationary scroll plate 32, the moving scroll plate 33 and the frame 36, forms a second pressure space 60. The pressure of the first pressure space 50 is greater than the pressure of the second pressure space 60. The first pressure space 50 is connected to the oil storage space 102. A medium pressure channel 325 is provided on the stationary scroll plate 32. The medium pressure channel 325 is connected to the compression chamber 301 and the second pressure space 60.

[0085] Specifically, in this embodiment, the intermediate pressure channel 325 connects the compression chamber 301 and the second pressure space 60, while the first pressure space 50 connects to the oil storage space 102. This arrangement is a method to establish a back pressure environment on the back of the moving scroll plate 33. By connecting the second pressure space 60 to the compression chamber 301 through the intermediate pressure channel 325, the pressure in the compression chamber 301 is higher than the compressor suction pressure, thereby making the pressure in the second pressure space 60 greater than the suction pressure, thus forming a back pressure. This back pressure can be the pressure on the moving scroll plate. The overturning mechanism of cylinder 33 provides support; the first pressure space 50 is connected to the oil storage space 102 to guide lubricating oil to the compression chamber 301 and various lubrication points. The lubricating oil at the bottom of the accommodating chamber 101 first flows through the crankshaft 31 to the bearings, then reaches the first pressure space 50, and then flows to the second pressure space 60 to lubricate the support boss 366 and the anti-rotation component 35. Subsequently, it flows into the compression chamber 301 through the intermediate pressure channel 325 to lubricate the first scroll gear 321 and the second scroll gear 331. Therefore, the lubricating oil in this embodiment can lubricate all contact friction points, thereby ensuring a high level of compressor reliability and friction performance.

[0086] Furthermore, in this embodiment, the pressure in the first pressure space 50 is greater than the pressure in the second pressure space 60. That is, the pressure in the inner space of the third annular groove 43 in this embodiment is higher than the pressure in the outer space. Thus, the first pressure space 50 can provide appropriate pressure to the second pressure space 60, thereby effectively suppressing the overturning of the moving vortex disk 33.

[0087] Further, see Figure 14 As shown, in this embodiment, the third annular groove 43 divides the sealing boss 365 into a first boss 3651 and a second boss 3652. The first boss 3651 is closer to the second bearing hole 362 than the second boss 3652. Along the axial direction of the crankshaft 31, the distance H5 between the first boss 3651 and the bottom of the receiving groove 364 is (e.g., ...). Figure 14 (As shown) is less than the distance H6 between the second boss 3652 and the bottom of the receiving groove 364 (as shown) Figure 14 As shown), and the distance H7 between the first boss 3651 and the extended surface of the end face of the supporting boss 366 near the moving scroll disk 33 (as shown). Figure 14 As shown, the following relationship is satisfied: 0.5mm≤H7≤1mm. For example, H7 can be set to 0.5mm, 0.55mm, 0.6mm, 0.65mm, 0.7mm, 0.75mm, 0.8mm, 0.85mm, 0.9mm, 0.95mm, 1mm, etc.

[0088] Specifically, since the second protrusion 3652 in this embodiment is closer to the side of the moving scroll plate 33 away from the stationary scroll plate 32 than the first protrusion 3651, the height of the outer side wall of the third annular groove 43 away from the second bearing hole 362 is higher than the height of the inner side wall of the third annular groove 43 near the second bearing hole 362. Under the pressure difference between the first pressure space 50 and the second pressure space 60, the seal 34 will be expanded so that the seal 34 fits against the outer side wall of the third annular groove 43, thereby improving the sealing effect of the seal 34.

[0089] Meanwhile, in this embodiment, by ensuring that the distance H7 between the extension surface of the first boss 3651 and the end face of the supporting boss 366 near the moving scroll plate 33 satisfies the relationship: 0.5mm≤H7≤1mm, it can be guaranteed that the sealing member 34 has sufficient axial clamping force to fit against the side of the moving scroll plate 33 away from the stationary scroll plate 32, and the pressure in the first pressure space 50 and the second pressure space 60 is different.

[0090] Furthermore, the rated cooling capacity Q of the air conditioning system in this embodiment satisfies the relationship: 2500W≤Q≤3700W. For example, Q can be set to 2500W, 2600W, 2700W, 2800W, 2900W, 3000W, 3100W, 3200W, 3300W, 3400W, 3500W, 3600W, 3700W, etc.

[0091] Furthermore, along the radial direction of the crankshaft 31, the maximum radial dimension D5 of the stator 22 in this embodiment (e.g.) Figure 1 As shown, the following relationship is satisfied: 96mm≤D5≤104mm. For example, D5 can be set to 96mm, 97mm, 98mm, 99mm, 100mm, 101mm, 102mm, 103mm, 104mm, etc.

[0092] Specifically, to meet the power requirements of the compressor and prevent reliability issues, the size of the motor 20 cannot be too small. While a larger motor 20 generally improves compressor efficiency, the improvement in efficiency diminishes after a certain point, leading to a decrease in cost-effectiveness. Therefore, the size of the motor 20 is limited. The size of the motor 20 is determined by the maximum radial dimension and height of the stator 22. Considering the significant impact of the ratio of the stator 22's maximum radial dimension to its height on compressor efficiency, and the fact that an excessively tall stator 22 would result in an excessively tall rotor 21, causing significant bending and deformation of the crankshaft 31 during operation and generating noise, the maximum radial dimension and height of the stator 22 are limited, taking into account reliability, cost-effectiveness, and noise levels. To meet the needs of air conditioning systems with cooling capacities ranging from 2500W to 3700W, this embodiment ensures that the maximum radial dimension D5 of the stator 22 satisfies the relationship: 96mm ≤ D5 ≤ 104mm.

[0093] Furthermore, along the radial direction of the crankshaft 31, the maximum radial dimension D6 of the moving scroll disk 33 in this embodiment (e.g.) Figure 4 As shown, the following relationship is satisfied: 78mm≤D6≤82mm. For example, D6 can be set to 78mm, 78.5mm, 79mm, 79.5mm, 80mm, 80.5mm, 81mm, 81.5mm, 82mm, etc.

[0094] 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. Based on this, in this embodiment, the maximum radial dimension D6 of the moving scroll plate 33 must be greater than or equal to 78mm; 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 D6 of the moving scroll plate 33 must be less than or equal to 82mm.

[0095] Further, see Figure 1 As shown, the compressor in this embodiment also includes a liquid receiver 70, which is connected to the intake pipe 11.

[0096] Specifically, the receiver 70 stores refrigerant, which enters the pump assembly 30 through the intake pipe 11. When the motor 20 drives the crankshaft 31 to rotate, it drives the eccentric section 312 to rotate, thereby driving the moving scroll plate 33 to rotate synchronously. This, in turn, drives the stationary scroll plate 32 to rotate relative to the moving scroll plate 33, compressing the refrigerant entering the compression chamber 301 from the outside, effectively improving the compressor's energy efficiency. At the same time, the refrigerant compressed by the pump assembly 30 is discharged into the receiving chamber 101 and discharged to the outside of the compressor through the exhaust pipe 12.

[0097] Further, see Figures 5 to 6As shown, the stationary scroll plate 32 in this embodiment is also provided with an intake port 326 and an exhaust port 327. The intake port 326 is connected to the intake pipe 11 and the compression chamber 301, and the exhaust port 327 is connected to the receiving chamber 101. With this configuration, the refrigerant in the liquid receiver 70 can enter from the intake pipe 11 and enter the compression chamber 301 through the intake port 326. After being compressed, the refrigerant in the compression chamber 301 is discharged into the receiving chamber 101 through the exhaust port 327.

[0098] 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.

[0099] 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.

[0100] 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.

[0101] 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 in the accommodating cavity (101) and is disposed closer to the bottom of the accommodating 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 frame (36). The crankshaft (31) is rotatably disposed in the accommodating cavity (101). The stationary scroll plate (32) is provided with a first scroll tooth (321) on the side near the moving scroll plate (33). The moving scroll plate (33) is provided with a second scroll tooth (331) that meshes with the first scroll tooth (321). The first scroll tooth (321) and the second scroll tooth (331) mesh to form a compression cavity (301). The housing (10) is provided with an intake pipe (11) and an exhaust pipe (12). The intake pipe (11) is connected to the compression chamber (301), and the exhaust pipe (12) is connected to the accommodating chamber (101). The crankshaft (31) includes a first shaft section (311), an eccentric section (312), and a second shaft section (313). The first shaft section (311) is located on the side of the eccentric section (312) close 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 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 frame (36) is located away from the... A second bearing portion (361) is provided on one side of the moving scroll plate (33), the second bearing portion (361) has a second bearing hole (362), the moving scroll plate (33) has an eccentric bearing hole (332), the motor (20) is driven and connected to the crankshaft (31), the stationary scroll plate (32) is sleeved on the first shaft segment (311) or the second shaft segment (313) through the first bearing hole (323), the moving scroll plate (33) is sleeved on the eccentric segment (312) through the eccentric bearing hole (332), the frame (36) is sleeved on the second shaft segment (313) or the first shaft segment (311) through the second bearing hole (362), and the anti-rotation component (35) is provided between the moving scroll plate (33) and the frame (36); The stationary scroll plate (32) has a first plane (324) on the side near the moving scroll plate (33), and the frame (36) has a second plane (363) on the side near the moving scroll plate (33). The second plane (363) fits against the first plane (324). A receiving groove (364) is formed on the second plane (363). A sealing boss (365) and a supporting boss (366) are provided in the receiving groove (364). Both the sealing boss (365) and the supporting boss (366) protrude from the bottom of the receiving groove (364). The sealing boss (365) and the supporting boss (366) are coaxially arranged and arranged in sequence from the inside to the outside along the radial direction of the crankshaft (31). The sealing element (34) is located between the sealing boss (365) and the moving scroll (33). The second bearing hole (362) passes through the sealing boss (365) along the axial direction of the crankshaft (31). The distance between the sealing boss (365) and the end face of the moving scroll (33) near the frame (36) is greater than the distance between the supporting boss (366) and the end face of the moving scroll (33) near the frame (36).

2. The compressor for use in an air conditioning system according to claim 1, characterized in that, Along the radial direction of the crankshaft (31), the minimum distance D1 between the center of the support boss (366) and the center of the second bearing hole (362) satisfies the relationship: D1≥30mm.

3. The compressor for use in an air conditioning system according to claim 1, characterized in that, The moving scroll disk (33) includes a moving disk base plate (333), and the second scroll tooth portion (331) is disposed on the side of the moving disk base plate (333) near the stationary scroll disk (32); Along the axial direction of the crankshaft (31), the minimum distance between the support boss (366) and the second plane (363) is H1, and the thickness of the moving disk substrate (333) is T1, wherein H1 and T1 satisfy the relationship: 0.01mm≤H1-T1≤0.025mm.

4. The compressor for use in an air conditioning system according to claim 1, characterized in that, Along the axial direction of the crankshaft (31), the distance between the sealing boss (365) and the bottom of the receiving groove (364) is H2, and the distance between the supporting boss (366) and the bottom of the receiving groove (364) is H3, wherein H2 and H3 satisfy the relationship: 0.05mm≤H3-H2≤0.5mm.

5. The compressor for use in an air conditioning system according to claim 1, characterized in that, The support boss (366) is arranged around the second bearing hole (362) in the receiving groove (364) in the circumferential direction. The support boss (366) is provided with a plurality of grooves (40), which are spaced apart in the circumferential direction of the support boss (366) to divide the support boss (366) into a plurality of support segments (37).

6. The compressor for use in an air conditioning system according to claim 5, characterized in that, Each of the support segments (37) has a first end and a second end. The line connecting the end of each first end to the center of the second bearing hole (362) is a first straight line (371), and the line connecting the end of each second end to the center of the second bearing hole (362) is a second straight line (372). An angle is formed between each first straight line (371) and each second straight line (372), and the sum of the angles is greater than or equal to 180°.

7. The compressor for use in an air conditioning system according to claim 5, characterized in that, Within the projection along the axial direction of the crankshaft (31), the sum of the projected areas of each of the support segments (37) is greater than and equal to 300 mm. 2 .

8. The compressor for use in an air conditioning system according to claim 1, characterized in that, Along the radial direction of the crankshaft (31), the minimum distance between the support boss (366) and the center of the second bearing hole (362) is L, the eccentricity of the eccentric section (312) is e, and the maximum radial dimension of the moving scroll disk (33) is P, wherein L, e and P satisfy the relationship: P / 2-Le≥1.5mm.

9. The compressor for use in an air conditioning system according to claim 1, characterized in that, When the crankshaft (31) drives the moving scroll disk (33) to rotate and translate, the minimum distance D2 between the outer edge of the moving scroll disk (33) and the second plane (363) along the radial direction of the crankshaft (31) satisfies the relationship: D2≥0.2mm.

10. The compressor for use in an air conditioning system according to claim 1, characterized in that, The support boss (366) is circumferentially arranged around the second bearing hole (362) in the receiving groove (364). A first annular groove (41) is provided between the support boss (366) and the side wall of the receiving groove (364). The first annular groove (41) is circumferentially arranged around the support boss (366) and radially along the crankshaft (31). The minimum width D3 of the first annular groove (41) satisfies the relationship: D3≥1mm.

11. The compressor for use in an air conditioning system according to claim 10, characterized in that, Along the axial direction of the crankshaft (31), the distance H4 between the end face of the support boss (366) near the moving scroll disk (33) and the bottom of the first annular groove (41) satisfies the following relationship: H4≥0.2mm.

12. The compressor for use in an air conditioning system according to claim 1, characterized in that, The moving scroll plate (33) includes a moving plate base plate (333), and the second scroll tooth portion (331) is disposed on the side of the moving plate base plate (333) near the stationary scroll plate (32). The moving plate base plate (333) is provided with a second annular groove (42), which is disposed around the outer peripheral side of the moving plate base plate (333) along the circumference of the crankshaft (31). The cross-sectional area S of the second annular groove (42) satisfies the relationship: S≥1mm 2 .

13. The compressor for use in an air conditioning system according to claim 1, characterized in that, The first plane (324) and the second plane (363) are fitted together and have an overlapping sealing surface (44). The minimum width D4 of the overlapping sealing surface (44) along the radial direction of the crankshaft (31) satisfies the relationship: D4≥2mm.

14. The compressor for use in an air conditioning system according to claim 1, characterized in that, The sealing boss (365) is provided with a third annular groove (43), which is arranged around the second bearing hole (362) on the end face of the sealing boss (365) near the moving scroll plate (33). The sealing member (34) is provided in the third annular groove (43). The side of the sealing member (34) near the crankshaft (31) is surrounded by the moving scroll plate (33) and the frame (36) to form a first pressure space (50). The side of the sealing member (34) away from the crankshaft (31) is surrounded by the stationary scroll plate (32), the moving scroll plate (33) and the frame (36) to form a second pressure space (60). The pressure of the first pressure space (50) is greater than the pressure of the second pressure space (60). The first pressure space (50) is connected to the oil storage space (102). The stationary vortex disk (32) is provided with a medium pressure channel (325), which is connected to the compression chamber (301) and the second pressure space (60).

15. The compressor for use in an air conditioning system according to claim 14, characterized in that, The third annular groove (43) divides the sealing boss (365) into a first boss (3651) and a second boss (3652). The first boss (3651) is closer to the second bearing hole (362) than the second boss (3652). Along the axial direction of the crankshaft (31), the distance H5 between the first boss (3651) and the bottom of the receiving groove (364) is less than the distance H6 between the second boss (3652) and the bottom of the receiving groove (364). The distance H7 between the first boss (3651) and the extended surface of the end face of the support boss (366) near the moving scroll plate (33) satisfies the relationship: 0.5mm≤H7≤1mm.

16. The compressor for use in an air conditioning system according to any one of claims 1 to 15, characterized in that, The rated cooling capacity Q of the air conditioning system satisfies the following relationship: 2500W≤Q≤3700W.

17. The compressor for use in an air conditioning system according to any one of claims 1 to 15, characterized in that, Along the radial direction of the crankshaft (31), the maximum radial dimension D5 of the stator (22) satisfies the relationship: 96mm ≤ D5 ≤ 104mm; and / or, Along the radial direction of the crankshaft (31), the maximum radial dimension D6 of the moving scroll disk (33) satisfies the relationship: 78mm≤D6≤82mm.

18. 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 17.

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