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 comprises a casing, a motor and a pump body assembly. The motor comprises a rotor and a stator; the pump body assembly comprises a crankshaft, a static scroll disc, a dynamic scroll disc, a support and an anti-rotation device. The static scroll disc is provided with a first scroll tooth portion, and the dynamic scroll disc is provided with a second scroll tooth portion. The side, away from the dynamic scroll disc, of the static scroll disc is provided with a first bearing portion, the first bearing portion is provided with a first bearing hole; the side, away from the dynamic scroll disc, of the support is provided with a second bearing portion, the second bearing portion is provided with a second bearing hole; the dynamic scroll disc is provided with an eccentric bearing hole; the crankshaft comprises a first shaft section, an eccentric section and a second shaft section; the motor is sleeved on the first shaft section; the static scroll disc is sleeved on the first shaft section or the side, close to the eccentric section, of the second shaft section through the first bearing hole; the dynamic scroll disc is sleeved on the eccentric section through the eccentric bearing hole; and the support is sleeved on the side, close to the eccentric section, of the first shaft section or the second shaft section through the second bearing hole.

Description

Technical Field

[0001] This application relates to the field of refrigeration technology, and more specifically, to a compressor and an air conditioning system for use in an air conditioning system. Background Technology

[0002] Air conditioners are high-power appliances, and users are increasingly demanding higher energy efficiency from them. As the core component of an air conditioner, the compressor's energy efficiency has a significant impact on the overall energy efficiency of the air conditioner.

[0003] Existing compressors typically include rolling rotor compressors and scroll compressors. Among them, scroll compressors have higher volumetric efficiency and less leakage, resulting in higher energy efficiency compared to rolling rotor compressors. However, existing scroll compressors generally adopt a pump-on-top structure, meaning the pump body is placed above the motor. This means that the pump body has only one bearing supporting the crankshaft, requiring an additional bearing below the motor to support the crankshaft. Furthermore, because the pump body is far from the bottom oil sump, a bushing is needed at the bearing to ensure reliable operation of the scroll compressor. Consequently, the structure of scroll compressors is more complex than that of rolling rotor compressors, leading to higher manufacturing costs. 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 of low cost-effectiveness of scroll compressors in the prior art.

[0005] According to one aspect of this application, a compressor for use in an air conditioning system is provided. The air conditioning system includes a refrigerant, an evaporator, a condenser, a throttling device, and the compressor. The rated cooling capacity CC of the air conditioning system satisfies the relationship: 2500W ≤ CC ≤ 3700W. The compressor includes a vertical variable frequency scroll compressor, and further includes:

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

[0007] An electric motor is disposed within the accommodating cavity, and the electric motor includes a rotor and a stator sleeved on the outer periphery of the rotor;

[0008] A pump body assembly is disposed within the accommodating cavity and near the bottom of the accommodating cavity. The pump body assembly includes a crankshaft, a stationary scroll plate, a moving scroll plate, a bracket, and an anti-rotation device. The crankshaft is rotatably disposed within the accommodating cavity and passes through the motor, the stationary scroll plate, the moving scroll plate, and the bracket. The stationary scroll plate has a first scroll tooth on the side near the moving scroll plate, and the moving scroll plate has a second scroll tooth that meshes with the first scroll tooth. The first scroll tooth and the second scroll tooth mesh to form a compression cavity.

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

[0010] Furthermore, the maximum radial dimension D1 of the stator satisfies the relationship: 96mm ≤ D1 ≤ 104mm; and / or,

[0011] The maximum radial dimension D2 of the moving scroll disk satisfies the following relationship: 76mm≤D2≤84mm.

[0012] Furthermore, the maximum radial dimension D1 of the stator satisfies the relationship: 98mm ≤ D1 ≤ 102mm; and / or,

[0013] The maximum radial dimension D2 of the moving scroll disk satisfies the following relationship: 78mm≤D2≤82mm.

[0014] Furthermore, the diameter D3 of the eccentric bearing hole satisfies the following relationship: 14mm≤D3≤18mm.

[0015] Furthermore, the second vortex tooth is spirally arranged around the outer periphery of the eccentric bearing hole. The second vortex tooth includes a vortex bearing, a first vortex head end, a first vortex body, and a first vortex tail end. The vortex bearing, the first vortex head end, the first vortex body, and the first vortex tail end are arranged sequentially along the spiral direction of the second vortex tooth itself. The vortex bearing has the eccentric bearing hole.

[0016] Furthermore, taking the center of the eccentric bearing hole as the starting point, a tangent OA is drawn to the first end of the first vortex, and a tangent OB is drawn to the tail end of the first vortex, taking the center of the eccentric bearing hole as the starting point. Along the spiral winding direction from the first end of the first vortex to the tail end of the first vortex, the included angle θ1 between OA and OB satisfies the relationship: 220°≤θ1≤330°.

[0017] Furthermore, taking the center of the eccentric bearing hole as the starting point, a tangent OA is drawn to the first end of the first vortex, and a tangent OB is drawn to the tail end of the first vortex, taking the center of the eccentric bearing hole as the starting point. Along the spiral winding direction from the first end of the first vortex to the tail end of the first vortex, the included angle θ1 between OA and OB satisfies the relationship: 240°≤θ1≤310°.

[0018] Furthermore, the minimum distance between the side of the tail end of the first vortex near the outer edge of the moving vortex disk and the outer edge of the moving vortex disk is S1;

[0019] The opposite extension of the tangent OB between the center of the eccentric bearing hole and the tail end of the first vortex is OC. OC and the first vortex roll body have multiple first intersection points. Among the multiple first intersection points, the minimum distance between the first intersection point farther from the center of the eccentric bearing hole and the outer edge of the moving vortex disk is S2.

[0020] Among them, S1 and S2 satisfy the relationship: |S1-S2|≤1.5mm.

[0021] Furthermore, the point closest to the first vortex head end and the eccentric bearing hole is D, and the line connecting point D and the center of the eccentric bearing hole is OD;

[0022] The intersection point E between the reverse extension of OD and the outer wall of the scroll bearing;

[0023] Wherein, the minimum distance between point D and the eccentric bearing hole is G1, and the minimum distance between point E and the eccentric bearing hole is G2. G1 and G2 satisfy the relationship: |G1-G2|≤1.5mm.

[0024] Furthermore, the first vortex tooth is spirally arranged around the outer periphery of the first bearing hole, and the minimum distance S between the side wall of the first vortex tooth near the center of the first bearing hole and the outer edge of the moving vortex disk satisfies the relationship: 1.5mm≤S≤3.5mm.

[0025] Furthermore, the minimum distance G between the hole wall of the eccentric bearing hole and the inner wall surface of the second vortex tooth near the eccentric bearing hole satisfies the following relationship: 1.5mm≤G≤3.5mm.

[0026] Furthermore, the vortex profile of the second vortex tooth includes the involute of the base circle.

[0027] Furthermore, there is a predetermined distance C between the center point of the base circle of the vortex profile and the center point of the eccentric bearing hole, wherein C satisfies the relationship: C≥2mm.

[0028] Furthermore, one of the static vortex disk and the bracket is provided with a threaded hole adapted to the locking member, and the other is provided with a through hole for the locking member to pass through. The threaded hole and the multiple through holes are provided correspondingly, and the locking member passes through both the corresponding threaded hole and the through hole.

[0029] Furthermore, when the pump body assembly is in operation, the minimum radial distance S3 between the outer edge of the moving scroll disk and the through hole satisfies the following relationship: 1.8mm≤S3≤2.8mm.

[0030] Furthermore, the diameter D4 of the through hole satisfies the following relationship: D4≤4.6mm.

[0031] Furthermore, each of the threaded holes and the through holes includes at least five, with each threaded hole and each through hole being provided in a one-to-one correspondence;

[0032] Wherein, at least five of the threaded holes are spaced apart circumferentially along the crankshaft on the stationary scroll plate, and at least five of the through holes are spaced apart circumferentially along the crankshaft on the bracket; or,

[0033] At least five threaded holes are spaced apart circumferentially along the crankshaft on the bracket, and at least five through holes are spaced apart circumferentially along the crankshaft on the stationary vortex disk.

[0034] Furthermore, the stationary scroll plate has an exhaust port that connects the accommodating cavity and the compression cavity. The stationary scroll plate is located on the side of the moving scroll plate near the motor, and the bracket is located on the side of the moving scroll plate away from the motor.

[0035] Furthermore, the refrigerant includes R32 refrigerant or R290 refrigerant;

[0036] When the refrigerant includes R32 refrigerant, the compressor displacement V1 satisfies the following relationship: 8cm 3 ≤V1≤12cm 3 ;or,

[0037] When the refrigerant includes R290 refrigerant, the compressor displacement V2 satisfies the following relationship: 16cm 3 ≤V2≤24cm 3 .

[0038] Furthermore, the compressor also includes a liquid receiver, and the housing has an air inlet and an air outlet. The air inlet is connected to the liquid receiver and the compression chamber, and the air outlet is connected to the accommodating chamber and the outside.

[0039] The liquid storage volume V3 of the liquid reservoir satisfies the relationship 300mL≤V3≤500mL.

[0040] Furthermore, the anti-rotation device includes a cross slip ring, which is installed between the moving scroll plate and the support; and / or,

[0041] The housing is provided with terminals for connecting the motor and an external power supply.

[0042] On the other hand, this application also provides an air conditioning system, which includes the compressor described above for use in air conditioning systems.

[0043] Because the stationary scroll plate in this application has a first bearing portion and the bracket has a second bearing portion, and the pump body assembly is closer to the bottom of the receiving cavity than the motor, i.e., the compressor adopts a bottom-mounted pump body assembly structure, the presence of the first and second bearing portions can support the crankshaft, thus eliminating the need for an additional bearing on the other side of the motor to support the crankshaft. Simultaneously, the first and second bearing portions are closer to the lubricating oil at the bottom of the receiving cavity, thus eliminating the need for additional bushings to ensure reliable compressor operation. The overall structure is simple and the manufacturing cost is low. Furthermore, because the first and second scroll teeth in this application mesh to form a compression chamber, which includes multiple sub-chambers, leakage between the sub-chambers is minimal, effectively improving the compressor's energy efficiency. Attached Figure Description

[0044] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments of this application and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings:

[0045] Figure 1 This is a cross-sectional view of the compressor disclosed in an embodiment of this application;

[0046] Figure 2 This is an exploded view of the pump body assembly disclosed in the embodiments of this application;

[0047] Figure 3 This is a cross-sectional view of the moving scroll disk disclosed in the embodiments of this application;

[0048] Figure 4 This is a cross-sectional view of the stationary vortex disk disclosed in the embodiments of this application;

[0049] Figure 5 This is a cross-sectional view of the bracket disclosed in an embodiment of this application;

[0050] Figure 6 This is a schematic diagram of the structure of the moving vortex disk disclosed in the embodiments of this application;

[0051] Figure 7 This is a schematic diagram of the structure of the second vortex tooth section disclosed in the embodiment of this application, where the vortex profile is not biased.

[0052] Figure 8 This is a schematic diagram of the structure when the moving scroll plate and the stationary scroll plate are meshing, as disclosed in the embodiments of this application;

[0053] Figure 9 This is a schematic diagram of a structure in which the center of the base circle and the center of the eccentric bearing hole do not coincide, as disclosed in an embodiment of this application.

[0054] Figure 10 This is a schematic diagram of a static vortex disk or support with through holes disclosed in an embodiment of this application.

[0055] Figure 11 This is a schematic diagram of the structure when the first and second vortex teeth disclosed in the embodiments of this application are engaged.

[0056] The above figures include the following reference numerals:

[0057] 10. Housing; 101. Receptacle; 102. Oil reservoir; 11. Air inlet; 12. Air outlet; 20. Motor; 21. Rotor; 22. Stator; 30. Pump assembly; 301. Compression chamber; 302. First compression chamber; 303. Second compression chamber; 31. Crankshaft; 311. First shaft section; 312. Eccentric section; 313. Second shaft section; 32. Stationary scroll plate; 321. First scroll gear section; 322. First bearing section; 3221 323. First bearing hole; 33. Exhaust hole; 34. Moving scroll plate; 35. Second scroll tooth section; 36. Eccentric bearing hole; 37. Scroll bearing; 38. First scroll head end; 39. First scroll body; 30. First scroll tail end; 31. Base circle; 32. Support; 33. Second bearing section; 34.11. Second bearing hole; 35. Anti-rotation device; 46. Threaded hole; 57. Through hole; 68. Liquid reservoir; 79. Terminal block. Detailed Implementation

[0058] 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.

[0059] 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.

[0060] 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.

[0061] See Figures 1 to 11 As shown, according to an embodiment of this application, a compressor for use in an air conditioning system is provided. The air conditioning system includes a refrigerant, an evaporator, a condenser, a throttling device, and a compressor. The rated cooling capacity CC of the air conditioning system satisfies the relationship: 2500W ≤ CC ≤ 3700W. The compressor includes a vertical variable frequency scroll compressor, and further includes a casing 10, a motor 20, and a pump assembly 30. Exemplarily, CC in this embodiment can be set to 2500W, 2600W, 2700W, 2800W, 2900W, 3000W, 3100W, 3200W, 3300W, 3400W, 3500W, 3600W, 3700W, etc.

[0062] 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 near the bottom of the receiving cavity 101, and the pump body assembly 30 includes a crankshaft 31, a stationary scroll plate 32, a moving scroll plate 33, a bracket 34, and a protective shield. The self-rotating device 35 and the crankshaft 31 are rotatably disposed in the accommodating cavity 101. The crankshaft 31 passes through the motor 20, the stationary scroll plate 32, the moving scroll plate 33 and the bracket 34. The stationary scroll plate 32 is provided with a first scroll tooth 321 on the side near the moving scroll plate 33. The moving scroll plate 33 is provided with a second scroll tooth 331 that meshes with the first scroll tooth 321. The first scroll tooth 321 and the second scroll tooth 331 mesh to form a compression cavity 301.

[0063] The stationary scroll plate 32 has a first bearing portion 322 on the side opposite to the moving scroll plate 33, and the first bearing portion 322 has a first bearing hole 3221. The bracket 34 has a second bearing portion 341 on the side opposite to the moving scroll plate 33, and the second bearing portion 341 has a second bearing hole 3411. The moving scroll plate 33 has an eccentric bearing hole 332. The crankshaft 31 includes a first shaft section 311, an eccentric section 312, and a second shaft section 313. The first shaft section 311, the eccentric section 312, and the second shaft section 313 are connected along... The crankshaft 31 is arranged sequentially along its axial direction. The motor 20 is fitted onto the first shaft section 311. The stationary scroll plate 32 is fitted onto the side of the first shaft section 311 near the eccentric section 312 or the side of the second shaft section 313 near the eccentric section 312 through the first bearing hole 3221. The moving scroll plate 33 is fitted onto the eccentric section 312 through the eccentric bearing hole 332. The bracket 34 is fitted onto the side of the first shaft section 311 near the eccentric section 312 or the side of the second shaft section 313 near the eccentric section 312 through the second bearing hole 3411.

[0064] In this embodiment, during the actual manufacturing of the compressor, the motor 20 and the pump assembly 30 can both be installed within the accommodating cavity 101, with the crankshaft 31 passing through the motor 20, the stationary scroll 32, the moving scroll 33, and the bracket 34. The motor 20 is driven by the crankshaft 31. When the motor 20 drives the crankshaft 31 to rotate, it drives the eccentric section 312 to rotate, thereby causing the moving scroll 33 to rotate synchronously. This, in turn, causes the stationary scroll 32 to rotate relative to the moving scroll 33, compressing the refrigerant entering the compression cavity 301.

[0065] It is understood that in this embodiment, the stationary scroll plate 32 may be sleeved on the side of the first shaft segment 311 near the eccentric segment 312 through the first bearing hole 3221, and the bracket 34 may be sleeved on the side of the second shaft segment 313 near the eccentric segment 312 through the second bearing hole 3411. Alternatively, the stationary scroll plate 32 may be sleeved on the side of the second shaft segment 313 near the eccentric segment 312 through the first bearing hole 3221, and the bracket 34 may be sleeved on the side of the first shaft segment 311 near the eccentric segment 312 through the second bearing hole 3411. The appendix of this embodiment... Figure 1 The diagram shows the case where the stationary vortex disk 32 is sleeved on the side of the first shaft segment 311 near the eccentric segment 312 through the first bearing hole 3221, and the bracket 34 is sleeved on the side of the second shaft segment 313 near the eccentric segment 312 through the second bearing hole 3411.

[0066] Meanwhile, since the stationary scroll plate 32 in this embodiment has a first bearing portion 322 and the bracket 34 has a second bearing portion 341, 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 341 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 341 are closer to the lubricating oil at the bottom of the receiving cavity 101, thus eliminating the need for an additional bushing to ensure reliable compressor operation. The overall structure is simple and the manufacturing cost is low. Furthermore, since the first scroll tooth portion 321 and the second scroll tooth portion 331 mesh to form the compression cavity 301 in this embodiment, which includes multiple sub-chambers, leakage between the sub-chambers is minimal, effectively improving the compressor's energy efficiency.

[0067] Furthermore, in this embodiment, the maximum radial dimension D1 of the stator 22 satisfies the relationship: 96mm≤D1≤104mm. For example, D1 can be set to 96mm, 97mm, 98mm, 99mm, 100mm, 101mm, 102mm, 103mm, 104mm, etc.

[0068] 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 motor's size 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 that an excessively high stator 22 would result in an excessively high rotor 21, causing significant bending 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 D1 of the stator 22 satisfies the relationship: 96mm ≤ D1 ≤ 104mm.

[0069] Furthermore, in this embodiment, the maximum radial dimension D2 of the moving scroll disk 33 satisfies the relationship: 76mm≤D2≤84mm. For example, D2 can be set to 76mm, 77mm, 78mm, 79mm, 80mm, 81mm, 82mm, 83mm, 84mm, etc.

[0070] Specifically, the moving scroll plate 33 is used to house the second scroll tooth 331 and needs to seal and cover the first scroll tooth 321 of the stationary scroll plate 32. The maximum radial dimension of the moving scroll plate 33 is related to the bore diameter of the eccentric bearing hole 332, the tooth thickness of the second scroll tooth 331, the eccentricity of the eccentric section 312, the number of scrolls of the second scroll tooth 331, and the sealing width. Smaller parameters result in smaller maximum radial dimensions of the moving scroll 33. However, excessively small bore diameter of the eccentric bearing hole 332 can lead to excessive surface pressure on the eccentric section 312, causing reliability issues. Insufficient tooth thickness of the second scroll tooth 331 can cause deformation, resulting in meshing friction or even breakage. Insufficient eccentricity can lead to excessive surface pressure on the first and second shaft sections 311 and 313 of the crankshaft 31, causing reliability problems. Insufficient scroll number of the second scroll tooth 331 makes it difficult to achieve a large volumetric ratio, leading to undercompression losses and reduced energy efficiency. Insufficient sealing width can cause excessive leakage, reducing compressor efficiency. Therefore, the maximum radial dimension of the moving scroll 33 needs to be limited. Considering the requirements of air conditioning systems with cooling capacities ranging from 2500W to 3700W, in this embodiment, the maximum radial dimension D2 of the moving scroll 33 must be greater than or equal to 76mm; otherwise, the compressor's energy efficiency and reliability 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, and the more materials are used, which reduces the cost-effectiveness of the compressor. Therefore, in this embodiment, the maximum radial dimension D2 of the moving scroll plate 33 must be less than or equal to 84mm.

[0071] Specifically, in this embodiment, the maximum radial dimension D1 of the stator 22 (e.g.) Figure 1 As shown, the following relationship is satisfied: 98mm≤D1≤102mm. For example, D1 can be set to 98mm, 98.5mm, 99mm, 99.5mm, 100mm, 100.5mm, 101mm, 101.5mm, 102mm, etc.

[0072] 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 motor's size 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 high stator 22 would result in an excessively high 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 D1 of the stator 22 satisfies the relationship: 98mm ≤ D1 ≤ 102mm.

[0073] Specifically, in this embodiment, the maximum radial dimension D2 of the moving scroll disk 33 (e.g.) Figure 3 As shown, the following relationship is satisfied: 78mm≤D2≤82mm. For example, D2 can be set to 78mm, 78.5mm, 79mm, 79.5mm, 80mm, 80.5mm, 81mm, 81.5mm, 82mm, etc.

[0074] 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 too small, it will be difficult to increase the volume ratio, which will cause the compressor to easily generate 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 needs to be limited. Considering the needs of air conditioning systems with a cooling capacity of 2500W to 3700W, in this embodiment, the maximum radial dimension D2 of the moving scroll 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, and the more materials are used, which reduces the cost-effectiveness of the compressor. Therefore, in this embodiment, the maximum radial dimension D2 of the moving scroll plate 33 must be less than or equal to 82mm.

[0075] Furthermore, in this embodiment, the diameter D3 of the eccentric bearing hole 332 (e.g.) Figure 3 As shown, the following relationship is satisfied: 14mm≤D3≤18mm. For example, D3 can be set to 14mm, 14.5mm, 15mm, 15.5mm, 16mm, 16.5mm, 17mm, 17.5mm, 18mm, etc.

[0076] Specifically, the diameter of the eccentric bearing bore 332 affects the reliability of the compressor. When D3 is less than 14mm, the diameter of the eccentric bearing bore 332 is too small, which can easily lead to excessive surface pressure on the eccentric section 312, thereby reducing the reliability of the crankshaft 31. At the same time, with the eccentricity of the eccentric section 312 remaining constant, the smaller the diameter of the eccentric bearing bore 332, the smaller at least one of the first shaft section 311 and the second shaft section 313 must be, otherwise the crankshaft 31 cannot be inserted into the eccentric bearing bore 332. This reduces the reliability of the first shaft section 311 and the second shaft section 313, and also reduces the rigidity of the crankshaft 31. When D3 is greater than 18mm, the diameter of the eccentric bearing bore 332 is too large, which leads to an increase in the outer diameter of the moving scroll plate 33, which in turn leads to an increase in the amount of material used in the pump body assembly 30, reducing the cost-effectiveness of the compressor. In other words, in order to ensure the reliability of the compressor in an air conditioning system with a cooling capacity ranging from 2500W to 3700W, this embodiment ensures the reliability of the compressor and effectively improves its cost-effectiveness by making the diameter D3 of the eccentric bearing hole 332 satisfy the relationship: 14mm≤D3≤18mm.

[0077] Further, see Figure 6 As shown, the second vortex tooth 331 is spirally arranged around the outer periphery of the eccentric bearing hole 332. The second vortex tooth 331 includes a vortex bearing 333, a first vortex head end 334, a first vortex body 335, and a first vortex tail end 336. The vortex bearing 333, the first vortex head end 334, the first vortex body 335, and the first vortex tail end 336 are arranged sequentially along the spiral direction of the second vortex tooth 331 itself. The vortex bearing 333 has an eccentric bearing hole 332.

[0078] Specifically, in this embodiment, the eccentric bearing hole 332 of the scroll bearing 333 provides a precise support point for the moving scroll disk 33. In the compressor, the moving scroll disk 33 follows the eccentric section 312 to make eccentric movements. The setting of the eccentric bearing hole 332 can keep the moving scroll disk 33 stable during high-speed operation and reduce the shaking and offset caused by eccentric movements. The first scroll body 335 is the core part of the second scroll tooth 331. It is responsible for realizing the continuous compression of gas. As the moving scroll disk 33 rotates, the corresponding parts of the first scroll body 335 and the first scroll tooth 321 continuously approach and move away, so that the gas is compressed in the gradually shrinking space, effectively ensuring the stable increase of gas pressure in the compression chamber 301.

[0079] Furthermore, in this embodiment, a tangent OA is drawn from the center of the eccentric bearing hole 332 to the end of the first vortex head 334, and a tangent OB is drawn from the center of the eccentric bearing hole 332 to the end of the first vortex tail 336. Along the spiral winding direction from the first vortex head 334 to the first vortex tail 336, the included angle θ1 between OA and OB (e.g., ...) Figure 6 As shown, the following relationship is satisfied: 220°≤θ1≤330°. For example, θ1 can be set to 220°, 240°, 260°, 280°, 300°, 310°, 320°, 330°, etc.

[0080] Specifically, when θ1 is less than 220°, the overall length of the second scroll tooth 331 is short, resulting in fewer rotations. This makes the compressor prone to undercompression, leading to a decrease in compressor efficiency. When θ1 is greater than 330°, the overall length of the second scroll tooth 331 is long, resulting in more rotations. While this reduces the likelihood of undercompression loss, it increases processing time and costs, and also leads to an excessively large radial dimension of the moving scroll 33, resulting in a lower overall compressor cost-effectiveness. Therefore, considering the operating conditions of air conditioners with cooling capacities between 2500W and 3700W, i.e., the possibility of undercompression loss, this embodiment ensures that θ1 satisfies the relationship: 220°≤θ1≤330°. This prevents undercompression loss in the compressor and improves its cost-effectiveness.

[0081] Furthermore, in this embodiment, a tangent OA is drawn from the center of the eccentric bearing hole 332 to the end of the first vortex head 334, and a tangent OB is drawn from the center of the eccentric bearing hole 332 to the end of the first vortex tail 336. Along the spiral winding direction from the first vortex head 334 to the first vortex tail 336, the included angle θ1 between OA and OB (e.g., ...) Figure 6 As shown, the following relationship is satisfied: 240°≤θ1≤310°. For example, θ1 can be set to 240°, 250°, 260°, 270°, 280°, 290°, 300°, 310°, etc.

[0082] Specifically, when θ1 is less than 240°, the overall length of the second scroll tooth 331 is short, resulting in fewer rotations. This makes the compressor prone to undercompression, leading to a decrease in compressor efficiency. When θ1 is greater than 310°, the overall length of the second scroll tooth 331 is long, resulting in more rotations. While this reduces the likelihood of undercompression loss, it increases processing time and costs, and also leads to an excessively large radial dimension of the moving scroll 33, resulting in a lower overall compressor cost-effectiveness. Therefore, considering the operating conditions of air conditioners with cooling capacities between 2500W and 3700W, i.e., the possibility of undercompression loss, this embodiment ensures that θ1 satisfies the relationship: 240°≤θ1≤310°. This prevents undercompression loss in the compressor and improves its cost-effectiveness.

[0083] Furthermore, in this embodiment, the minimum distance between the side of the first vortex tail end 336 near the outer edge of the moving vortex disk 33 and the outer edge of the moving vortex disk 33 is S1 (e.g., Figure 6 (As shown); the reverse extension of the tangent OB between the center of the eccentric bearing hole 332 and the end of the first vortex tail 336 is OC. OC and the first vortex body 335 have multiple first intersection points. The minimum distance between the first intersection point farther from the center of the eccentric bearing hole 332 and the outer edge of the moving vortex disk 33 is S2 (as shown). Figure 6 (as shown); where S1 and S2 satisfy the relationship: |S1-S2|≤1.5mm, for example, |S1-S2| can be set to 1.5mm, 1.4mm, 1.2mm, 1mm, 0.8mm, 0.6mm, 0.4mm, 0.2mm, etc.

[0084] Specifically, in this embodiment, the shortest distance between the side of the first vortex tail end 336 near the outer edge of the moving vortex disk 33 and the outer edge of the moving vortex disk 33 is S1. A tangent OB is drawn from the center O of the eccentric bearing hole 332 to the end of the first vortex tail end 336. The last intersection point of the reverse extension of the tangent OB with the second vortex tooth 331 is point C. The shortest distance between point C and the outer edge of the moving vortex disk 33 is S2. The difference between S1 and S2 is less than or equal to 1.5 mm. This arrangement is because the moving vortex disk 33 has an eccentric bearing hole 332 at its center for the crankshaft 31 to pass through. Once the shape of the second vortex tooth 331 is determined, its placement on the moving vortex disk 33 determines the shortest distance S between the wall of the second vortex tooth 331 and the outer edge of the moving vortex disk 33, thereby ensuring the sealing effect of the pump body assembly 30.

[0085] Further, in this embodiment, the point closest to the first vortex head end 334 and the eccentric bearing hole 332 is D, and the line connecting point D and the center of the eccentric bearing hole 332 is OD; the intersection of the reverse extension of OD and the outer wall of the vortex bearing 333 is E; wherein, the minimum distance between point D and the eccentric bearing hole 332 is G1 (e.g., Figure 6 As shown), the minimum distance between point E and eccentric bearing hole 332 is G2 (as shown). Figure 6 As shown), G1 and G2 satisfy the relationship: |G1-G2|≤1.5mm. For example, |G1-G2| can be set to 1.5mm, 1.4mm, 1.2mm, 1mm, 0.8mm, 0.6mm, 0.4mm, 0.2mm, etc.

[0086] Specifically, in this embodiment, the point with the shortest distance between the side wall of the first vortex head end 334 near the center of the eccentric bearing hole 332 and the center of the eccentric bearing hole 332 is D. The shortest distance between point D and the eccentric bearing hole 332 is G1. The line connecting point D and the center O of the eccentric bearing hole 332 is OD. Extending OD in the opposite direction, the intersection of OD and the outer wall of the vortex bearing 333 is point E. The shortest distance between point E and the eccentric bearing hole 332 is G2. The difference between G1 and G2 is less than or equal to 1.5mm. This arrangement is because the center of the moving scroll disk 33 has an eccentric bearing hole 332 through which the crankshaft 31 passes. Once the shape of the second scroll tooth 331 is determined, the placement of the second scroll tooth 331 on the moving scroll disk 33 determines the shortest distance G between the side wall of the second scroll tooth 331 near the eccentric bearing hole 332 and the eccentric bearing hole 332, and also determines the minimum distance S between the side wall of the first scroll tooth 321 near the center of the first bearing hole 3221 and the outer edge of the moving scroll disk 33. Figure 6 and Figure 7 The maximum radial dimension of the moving scroll disk 33 is the same, and the second scroll tooth portion 331 is the same. When the placement position of the second scroll tooth portion 331 relative to the moving scroll disk 33 is different, from Figure 6 It is clear from the data that the shortest distances S and G are both greater than... Figure 7 The large one. Therefore. Figure 6 The moving scroll plate 33 in the middle has a higher space utilization rate, while the sealing effect in all directions is comparable. Specifically, the difference between G1 and G2 is small, and the difference between S1 and S2 is small.

[0087] Furthermore, in this embodiment, the first vortex tooth 321 is spirally arranged around the outer periphery of the first bearing hole 3221. The minimum distance S between the side wall surface of the first vortex tooth 321 near the center of the first bearing hole 3221 and the outer edge of the moving vortex disk 33 satisfies the relationship: 1.5mm ≤ S ≤ 3.5mm. For example, S can be set to 1.5mm, 2mm, 2.2mm, 2.4mm, 2.5mm, 2.6mm, 2.8mm, 3mm, 3.2mm, 3.4mm, 3.5mm, etc. It should be noted that in this embodiment... Figure 8 (a) shows a schematic diagram of the positional relationship between the first vortex tooth 321 and the moving vortex disk 33 in the first motion state; Figure 8 (b) shows a schematic diagram of the positional relationship between the first vortex tooth 321 and the moving vortex disk 33 in the second motion state.

[0088] Specifically, during the rotation of the crankshaft 31, the moving scroll 33 compresses the refrigerant in the compression chamber 301 to increase the gas pressure. During this compression, the moving scroll 33 experiences a reaction force from the gas pressure, causing it to be pushed away from the stationary scroll 32. Therefore, to ensure the moving scroll 33 and stationary scroll 32 are in close contact to guarantee the normal operation of the pump assembly 30, the side of the moving scroll 33 furthest from the second scroll tooth 331 needs to have a certain pressure to push it towards the stationary scroll 32. This pressure is called back pressure, which is between the suction pressure and the discharge pressure. The suction pressure is when the refrigerant is first drawn into the compression chamber 301. To prevent gas in the back pressure space from leaking into the compression chamber 301, a certain sealing distance must be maintained between the outer edge of the moving scroll 33 and the inner wall of the first scroll tooth 321. When S is less than 1.5mm, insufficient sealing distance will lead to gas leakage; when S is greater than 3.5mm, the radial dimension of the moving scroll plate 33 is too large, and too much material is used in the pump body assembly 30, reducing the cost-effectiveness of the compressor. In other words, in order to ensure the operation of air conditioners with cooling capacity in the range of 2500w to 3700w, this embodiment ensures the sealing effect of the pump body assembly 30 by satisfying the relationship: 1.5mm≤S≤3.5mm between the side wall surface of the first scroll tooth 321 near the center of the first bearing hole 3221 and the outer edge of the moving scroll plate 33. It should be noted that, since the first volute tooth 321 and the second volute tooth 331 mesh in this embodiment, the minimum distance S between the side wall of the first volute tooth 321 near the center of the first bearing hole 3221 and the outer edge of the moving volute disk 33 satisfies the relationship: 1.5mm≤S≤3.5mm, which has the same effect as controlling the minimum distance between the outer edge of the moving volute disk 33 and the side of the second volute tooth 331 near the outer edge of the moving volute disk 33.

[0089] Furthermore, in this embodiment, the minimum distance G between the wall of the eccentric bearing hole 332 and the inner wall surface of the second vortex tooth portion 331 near the eccentric bearing hole 332 (e.g., Figure 6 As shown, the following relationship is satisfied: 1.5mm≤G≤3.5mm. For example, G can be set to 1.5mm, 2mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, 3mm, 3.2mm, 3.4mm, 3.5mm, etc.

[0090] Specifically, in this embodiment, the point where the inner wall of the second vortex tooth 331 is closest to the eccentric bearing hole 332 is F, and the shortest distance from F to the eccentric bearing hole 332 is G. Point F may appear at the head end 334 of the first vortex or at other locations, as long as the shortest distance is satisfied.

[0091] During compressor operation, the center of the eccentric bearing bore 332 is under high pressure, while the pressure in the compression chamber 301 formed by the second scroll tooth 331 remains lower than the exhaust pressure for an extended period. To prevent fluid from flowing out of the compression chamber 301 from the connection between the moving scroll plate 33 and the crankshaft 31, thus causing gas leakage losses, and to ensure the structural strength of the second scroll tooth 331 under pressure differential, the distance between the second scroll tooth 331 and the eccentric bearing bore 332 should not be too small. When G is less than 1.5 mm, the distance between the second scroll tooth 331 and the eccentric bearing bore 332 is too short, making it difficult to guarantee the structural strength of the second scroll tooth 331, and fluid easily flows out of the compression chamber 301 from the connection between the moving scroll plate 33 and the crankshaft 31, resulting in gas leakage losses. When G is greater than 3.5 mm, the radial dimension of the moving scroll plate 33 increases, leading to excessive material usage in the pump body assembly 30 and reducing the compressor's cost-effectiveness. In other words, in order to meet the operating conditions of air conditioners with a cooling capacity ranging from 2500W to 3700W, this embodiment ensures that the minimum distance G between the center of the eccentric bearing hole 332 and the second scroll tooth 331 satisfies the relationship: 1.5mm≤G≤3.5mm. This reduces the loss of gas pressure in the compression chamber 301, effectively ensures the reliability and stability of the compressor's moving scroll 33 under harsh conditions, and improves the compressor's cost-effectiveness.

[0092] Further, see Figure 9 As shown, in this embodiment, the spiral profile of the second spiral tooth 331 includes the involute of the base circle 337. This configuration results in a simple structure and ease of manufacturing.

[0093] Specifically, the involute of the base circle 337 serves as the scroll profile for the second scroll tooth 331, which can cooperate with the first scroll tooth 321 to form a series of continuously varying compression chambers 301. During the operation of the compressor or pump assembly 30, as the moving scroll 33 rotates, the volume of these chambers gradually decreases, thereby compressing the fluid (such as refrigerant, gas, or liquid). Simultaneously, when the moving scroll 33 moves relative to the stationary scroll 32, the involute-based teeth can precisely follow the designed path, ensuring a good fit between the moving scroll 33 and the stationary scroll 32, thereby reducing leakage and effectively improving the compressor's compression efficiency.

[0094] Furthermore, in this embodiment, the center point of the base circle 337 of the vortex profile and the center point of the eccentric bearing hole 332 have a predetermined distance C (e.g., ...). Figure 9 As shown), where C satisfies the relationship: C≥2mm. For example, C can be set to 2mm, 2.2mm, 2.4mm, 2.6mm, 2.8mm, 3mm, 3.2mm, 3.4mm, 3.6mm, 3.8mm, 4mm, etc.

[0095] Specifically, in this embodiment, the aforementioned goal of minimizing the difference between s1 and s2, and the difference between g1 and g2, is achieved by ensuring that the center point of the base circle 337 of the profile does not coincide with the center point of the eccentric bearing hole 332. When C is less than 2mm, the movement space of the moving scroll 33 during eccentric motion is restricted, resulting in irregular vibrations and causing noise in the compressor. Simultaneously, insufficient spacing leads to a deterioration in the contact between the moving scroll 33 and the stationary scroll 32, potentially causing frequent friction between the scroll edges, or even collisions, shortening the compressor's lifespan.

[0096] Further, see Figure 2 as well as Figure 10 As shown, in this embodiment, one of the stationary scroll plate 32 and the bracket 34 is provided with a threaded hole 40 adapted to the locking member (not shown in the figure), and the other is provided with a through hole 50 for the locking member to pass through. The threaded hole 40 and multiple through holes 50 are correspondingly provided, and the locking member passes through both the corresponding threaded hole 40 and the through hole 50. Exemplarily, the locking member in this embodiment includes structures such as screws and studs. That is to say, in this embodiment, the stationary scroll plate 32 may be provided with a threaded hole 40 and the bracket 34 with a through hole 50, or the stationary scroll plate 32 may be provided with a through hole 50 and the bracket 34 with a threaded hole 40. The attached figure of this embodiment... Figure 2 The diagram shows the case where the stationary vortex disk 32 is provided with a threaded hole 40 and the bracket 34 is provided with a through hole 50.

[0097] It should be noted that, Figure 10 (c) shows a schematic diagram of the positional relationship between the moving scroll disk 33, which has moved to the first position, and the stationary scroll disk 32 or the support 34. Figure 10 (d) shows a schematic diagram of the positional relationship between the moving scroll 33, which has moved to the second position, and the stationary scroll 32 or the support 34.

[0098] Specifically, during the compressor assembly process, when assembling the stationary scroll plate 32 and the bracket 34, by having the locking element pass through the corresponding through hole 50 and threaded hole 40 simultaneously, the relative positions of the stationary scroll plate 32 and the bracket 34 within the accommodating cavity 101 can be ensured to be accurate, thereby improving the assembly speed and reducing assembly time and labor costs.

[0099] Furthermore, in this embodiment, when the pump body assembly 30 is operating, the minimum radial distance S3 between the outer edge of the moving scroll disk 33 and the through hole 50 (e.g., ...) is... Figure 10 As shown, the following relationship is satisfied: 1.8mm≤S3≤2.8mm. For example, S3 can be set to 1.8mm, 1.9mm, 2mm, 2.1mm, 2.2mm, 2.3mm, 2.4mm, 2.5mm, 2.6mm, 2.7mm, 2.8mm, etc.

[0100] Specifically, since the accommodating cavity 101 in this embodiment is a high-pressure environment, and the side of the moving scroll plate 33 away from the stationary scroll plate 32 is a back-pressure environment, in order to prevent high-pressure gas from leaking into the back-pressure environment through the gaps in the locking parts or the pressing surface between the stationary scroll plate 32 and the bracket 34, it is necessary to control the minimum distance between the through hole 50 and the outer edge of the moving scroll plate 33. When S3 is less than 1.8mm, the sealing distance between the moving scroll plate 33 and the stationary scroll plate 32 is insufficient, which can easily lead to gas leakage and reduce the energy efficiency of the compressor. When S3 is greater than 2.8mm, the diameter of the through hole 50 is too large, resulting in an increase in the maximum radial dimension of the stationary scroll plate 32 and the maximum radial dimension of the bracket 34, thereby leading to excessive material usage in the pump body assembly 30 and reducing the cost-effectiveness of the compressor.

[0101] Furthermore, in this embodiment, the diameter D4 of the through hole 50 (e.g.) Figure 10 As shown, the following relationship is satisfied: D4≤4.6mm. For example, D4 ​​can be set to 4.6mm, 4.4mm, 4.2mm, 4mm, 3.8mm, 3.6mm, 3.4mm, 3.2mm, 3mm, etc.

[0102] Specifically, considering further reducing the radial dimensions of the stationary vortex disk 32 and the bracket 34, this embodiment prefers a locking scheme with a small diameter but a large number of locking parts. Therefore, in this embodiment, by making the diameter D4 of the through hole 50 satisfy the relationship: D4≤4.6mm, a locking fit can be achieved with the locking parts with a smaller diameter.

[0103] Furthermore, in this embodiment, both the threaded holes 40 and the through holes 50 include at least five, with each threaded hole 40 corresponding to each through hole 50; wherein, at least five threaded holes 40 are spaced apart along the circumference of the crankshaft 31 on the stationary scroll plate 32, and at least five through holes 50 are spaced apart along the circumference of the crankshaft 31 on the bracket 34; or, at least five threaded holes 40 are spaced apart along the circumference of the crankshaft 31 on the bracket 34, and at least five through holes 50 are spaced apart along the circumference of the crankshaft 31 on the stationary scroll plate 32. Exemplarily, the appendix of this embodiment... Figure 2 The diagram shows a case where the stationary vortex disk 32 is provided with threaded holes 40 and the bracket 34 is provided with through holes 50, and there are six threaded holes 40 and six through holes 50.

[0104] Specifically, when at least five threaded holes 40 and through holes 50 are spaced apart along the circumference of the crankshaft 31, the connection force can be evenly distributed in the circumferential direction after the stationary volute 32 and the bracket 34 are connected, making the connection between the stationary volute 32 and the bracket 34 more secure and stable, effectively preventing loosening or deformation between the stationary volute 32 and the bracket 34 due to uneven force.

[0105] Further, see Figures 1 to 5 As shown, in this embodiment, the stationary scroll 32 has an exhaust port 323, which is connected to the accommodating cavity 101 and the compression cavity 301. The stationary scroll 32 is located on the side of the moving scroll 33 near the motor 20, and the bracket 34 is located on the side of the moving scroll 33 away from the motor 20.

[0106] Specifically, during the operation of the pump assembly 30, the refrigerant entering the compression chamber 301 from the outside is compressed and then discharged from the exhaust port 323 of the stationary scroll plate 32 into the receiving chamber 101. Compared with the prior art structure where the stationary scroll plate 32 is below the moving scroll plate 33, this embodiment places the stationary scroll plate 32 above the moving scroll plate 33, so that the refrigerant discharged from the exhaust port 323 appears above the pump assembly 30. There is no need to consider the isolation between the refrigerant and the lubricating oil at the bottom of the casing 10, and the overall structure is simple. At the same time, during the process of the refrigerant in the receiving chamber 101 being discharged from the exhaust port on the casing 10 to the outside of the compressor, the flow path of the refrigerant is shorter and the flow resistance is smaller, effectively improving the energy efficiency of the compressor.

[0107] Furthermore, the refrigerant in this embodiment includes R32 refrigerant or R290 refrigerant; wherein, when the refrigerant includes R32 refrigerant, the compressor displacement V1 satisfies the following relationship: 8cm 3 ≤V1≤12cm 3 For example, V1 can be set to 8cm. 3 8.5cm 3 9cm3 9.5cm 3 10cm 3 10.5cm 3 11cm 3 11.5cm 3 12cm 3 Alternatively, when the refrigerant includes R290 refrigerant, the compressor displacement V2 satisfies the following relationship: 16cm 3 ≤V2≤24cm 3 For example, V2 can be set to 16cm. 3 17cm 3 18cm 3 19cm 3 20cm 3 21cm 3 22cm 3 23cm 3 24cm 3 .

[0108] It should be noted that "R32 refrigerant" in this application includes difluoromethane refrigerant; "R290 refrigerant" includes propane refrigerant.

[0109] Specifically, in this embodiment, R32 refrigerant has a low global warming potential (GWP) and good cooling efficiency. When the compressor uses R32 refrigerant, to meet the needs of air conditioning systems with a cooling capacity in the range of 2500W to 3700W, the compressor displacement V1 needs to be set to greater than or equal to 8cm. 3 And less than or equal to 12cm 3 Among them, when V1 is less than 8cm 3 When the compressor displacement is too small, the compressor speed increases, which in turn increases the compressor noise and vibration; when V1 is greater than 12cm 3 At that time, the compressor's displacement was too large, which reduced the compressor's energy efficiency.

[0110] Meanwhile, R290 refrigerant also has a low global warming potential (GWP) and good cooling efficiency. When the compressor uses R290 refrigerant, to meet the needs of air conditioning systems with a cooling capacity in the range of 2500W to 3700W, the compressor displacement V2 needs to be set to greater than or equal to 16cm². 3 And less than or equal to 24cm 3 Among them, when V2 is less than 16cm 3 When the compressor displacement is too small, the compressor speed increases, which in turn increases the compressor noise and vibration; when V2 is greater than 24cm... 3At that time, the compressor's displacement was too large, which reduced the compressor's energy efficiency.

[0111] It should be noted that, in this embodiment, the compressor displacement is calculated as follows: Figure 11 As shown, Figure 11 The shaded area in (e) represents the maximum intake volume of the first compression chamber 302 formed by the meshing of the outer wall of the second vortex tooth 331 and the inner wall of the first vortex tooth 321 after intake is completed. Figure 11 The shaded area in (f) is the maximum intake volume of the second compression chamber 303 formed by the meshing of the inner wall of the second vortex tooth 331 and the outer wall of the first vortex tooth 321 after intake is completed. The sum of the two maximum intake volumes is the displacement of the compressor.

[0112] Further, see Figure 1 As shown, the compressor in this embodiment also includes a liquid reservoir 60. The housing 10 has an air inlet 11 and an air outlet 12. The air inlet 11 is connected to the liquid reservoir 60 and the compression chamber 301, and the air outlet 12 is connected to the accommodating chamber 101 and the outside. The liquid storage volume V3 of the liquid reservoir 60 satisfies the relationship 300mL≤V3≤500mL.

[0113] Specifically, the compressor is one of the core components of the air conditioning system, and its operation requires the participation of refrigerant. The receiver 60 can store a certain amount of liquid refrigerant. During the operation of the air conditioning system, when the refrigerant flow fluctuates or the compressor's suction demand suddenly increases, the receiver 60 can promptly provide sufficient refrigerant to replenish the system, ensuring the stable operation of the compressor.

[0114] When the air conditioning system operates under different conditions, its refrigerant requirements vary. In some cases, there may be excessive refrigerant, resulting in liquid refrigerant at the compressor inlet 11. Therefore, a liquid receiver 60 is needed to prevent liquid slugging in the compressor. Considering the operating conditions of air conditioning systems with refrigerant power ranging from 2500W to 3700W, and combining the compressor structure's anti-liquid slugging capability and the air conditioning's cost-effectiveness in this embodiment, the liquid receiver 60's storage volume V3 is controlled to satisfy the relationship 300mL ≤ V3 ≤ 500mL.

[0115] Further, see Figure 1 As shown, the anti-rotation device 35 in this embodiment includes a cross slip ring, which is installed between the moving scroll plate 33 and the support 34. This arrangement facilitates the limiting of the moving scroll plate 33, thereby preventing the moving scroll plate 33 from rotating.

[0116] Further, see Figure 1As shown, the housing 10 in this embodiment is provided with a terminal block 70 for connecting the motor 20 and an external power supply. Specifically, the terminal block 70 provides a stable electrical connection interface between the motor 20 and the external power supply. It ensures that the motor 20 can obtain a stable power supply, enabling the motor 20 to operate normally.

[0117] 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.

[0118] 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.

[0119] 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.

[0120] The above are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A compressor for use in an air conditioning system, the air conditioning system comprising a refrigerant, an evaporator, a condenser, a throttling device, and the compressor, wherein the rated cooling capacity CC of the air conditioning system satisfies the relationship: 2500W ≤ CC ≤ 3700W, and the compressor comprises a vertical variable frequency scroll compressor, characterized in that, The compressor also includes: The housing (10) has a receiving cavity (101), and the bottom of the receiving cavity (101) is provided with an oil storage space (102) for storing lubricating oil. The motor (20) is disposed in the accommodating cavity (101), and the motor (20) includes a rotor (21) and a stator (22) sleeved on the outer periphery of the rotor (21); A pump body assembly (30) is disposed within the receiving cavity (101) and near the bottom of the receiving cavity (101). The pump body assembly (30) includes a crankshaft (31), a stationary scroll plate (32), a moving scroll plate (33), a bracket (34), and an anti-rotation device (35). The crankshaft (31) is rotatably disposed within the receiving cavity (101), and the crankshaft (31) passes through the motor (20). The static scroll plate (32), the moving scroll plate (33), and the support (34) are described. The static 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 stationary scroll plate (32) has a first bearing portion (322) on the side opposite to the moving scroll plate (33), and the first bearing portion (322) has a first bearing hole (3221). The bracket (34) has a second bearing portion (341) on the side opposite to the moving scroll plate (33), and the second bearing portion (341) has a second bearing hole (3411). The moving scroll plate (33) has an eccentric bearing hole (332). The crankshaft (31) includes a first shaft section (311), an eccentric section (312), and a second shaft section (313). The first shaft section (311), the eccentric section (312), and the second shaft section (313) run along the crankshaft (33). 1) The axes are arranged sequentially, the motor (20) is sleeved on the first shaft segment (311), the stationary scroll plate (32) is sleeved on the side of the first shaft segment (311) near the eccentric segment (312) or the side of the second shaft segment (313) near the eccentric segment (312) through the first bearing hole (3221), the moving scroll plate (33) is sleeved on the eccentric segment (312) through the eccentric bearing hole (332), and the bracket (34) is sleeved on the side of the first shaft segment (311) near the eccentric segment (312) or the side of the second shaft segment (313) near the eccentric segment (312) through the second bearing hole (3411).

2. The compressor for use in an air conditioning system according to claim 1, characterized in that, The maximum radial dimension D1 of the stator (22) satisfies the following relationship: 96mm ≤ D1 ≤ 104mm; and / or, The maximum radial dimension D2 of the moving scroll disk (33) satisfies the following relationship: 76mm≤D2≤84mm.

3. The compressor for use in an air conditioning system according to claim 1, characterized in that, The maximum radial dimension D1 of the stator (22) satisfies the following relationship: 98mm ≤ D1 ≤ 102mm; and / or, The maximum radial dimension D2 of the moving scroll disk (33) satisfies the following relationship: 78mm≤D2≤82mm.

4. The compressor for use in an air conditioning system according to claim 1, characterized in that, The diameter D3 of the eccentric bearing hole (332) satisfies the following relationship: 14mm≤D3≤18mm.

5. The compressor for use in an air conditioning system according to claim 1, characterized in that, The second vortex tooth (331) is spirally arranged around the outer periphery of the eccentric bearing hole (332). The second vortex tooth (331) includes a vortex bearing (333), a first vortex head end (334), a first vortex body (335), and a first vortex tail end (336). The vortex bearing (333), the first vortex head end (334), the first vortex body (335), and the first vortex tail end (336) are arranged sequentially along the spiral direction of the second vortex tooth (331). The vortex bearing (333) has the eccentric bearing hole (332).

6. The compressor for use in an air conditioning system according to claim 5, characterized in that, Starting from the center of the eccentric bearing hole (332), draw a tangent OA to the end of the first vortex head (334), and starting from the center of the eccentric bearing hole (332), draw a tangent OB to the end of the first vortex tail (336). Along the spiral winding direction from the first vortex head (334) to the first vortex tail (336), the included angle θ1 between OA and OB satisfies the relationship: 220°≤θ1≤330°.

7. The compressor for use in an air conditioning system according to claim 5, characterized in that, Starting from the center of the eccentric bearing hole (332), draw a tangent OA to the end of the first vortex head (334), and starting from the center of the eccentric bearing hole (332), draw a tangent OB to the end of the first vortex tail (336). Along the spiral winding direction from the first vortex head (334) to the first vortex tail (336), the included angle θ1 between OA and OB satisfies the relationship: 240°≤θ1≤310°.

8. The compressor for use in an air conditioning system according to claim 5, characterized in that, The minimum distance between the side of the first vortex tail end (336) near the outer edge of the moving vortex disk (33) and the outer edge of the moving vortex disk (33) is S1; The reverse extension of the tangent OB between the center of the eccentric bearing hole (332) and the end of the first vortex tail (336) is OC. OC has multiple first intersection points with the first vortex body (335). The minimum distance between the first intersection point farther from the center of the eccentric bearing hole (332) and the outer edge of the moving vortex disk (33) is S2. Among them, S1 and S2 satisfy the relationship: |S1-S2|≤1.5mm.

9. The compressor for use in an air conditioning system according to claim 5, characterized in that, The point closest to the first vortex head end (334) and the eccentric bearing hole (332) is D, and the line connecting point D and the center of the eccentric bearing hole (332) is OD; The intersection point E between the reverse extension of OD and the outer wall of the vortex bearing (333); Among them, the minimum distance between point D and the eccentric bearing hole (332) is G1, and the minimum distance between point E and the eccentric bearing hole (332) is G2. G1 and G2 satisfy the relationship: |G1-G2|≤1.5mm.

10. The compressor for use in an air conditioning system according to claim 1, characterized in that, The first vortex tooth (321) is spirally arranged around the outer periphery of the first bearing hole (3221). The minimum distance S between the side wall of the first vortex tooth (321) near the center of the first bearing hole (3221) and the outer edge of the moving vortex disk (33) satisfies the relationship: 1.5mm≤S≤3.5mm.

11. The compressor for use in an air conditioning system according to claim 1, characterized in that, The minimum distance G between the wall of the eccentric bearing hole (332) and the inner wall surface of the second vortex tooth (331) near the eccentric bearing hole (332) satisfies the following relationship: 1.5mm≤G≤3.5mm.

12. The compressor for use in an air conditioning system according to claim 1, characterized in that, The vortex profile of the second vortex tooth (331) includes the involute of the base circle (337).

13. The compressor for use in an air conditioning system according to claim 12, characterized in that, There is a predetermined distance C between the center point of the base circle (337) of the vortex profile and the center point of the eccentric bearing hole (332), wherein C satisfies the relationship: C≥2mm.

14. The compressor for use in an air conditioning system according to claim 1, characterized in that, One of the static vortex disk (32) and the bracket (34) is provided with a threaded hole (40) adapted to the locking member, and the other is provided with a through hole (50) for the locking member to pass through. The threaded hole (40) and a plurality of through holes (50) are provided correspondingly, and the locking member passes through both the corresponding threaded hole (40) and the through hole (50).

15. The compressor for use in an air conditioning system according to claim 14, characterized in that, When the pump body assembly (30) is working, the minimum radial distance S3 between the outer edge of the moving scroll disk (33) and the through hole (50) satisfies the following relationship: 1.8mm≤S3≤2.8mm.

16. The compressor for use in an air conditioning system according to claim 14, characterized in that, The diameter D4 of the through hole (50) satisfies the following relationship: D4≤4.6mm.

17. The compressor for use in an air conditioning system according to claim 14, characterized in that, The threaded hole (40) and the through hole (50) each include at least five, and each threaded hole (40) is provided in a one-to-one correspondence with each through hole (50); At least five of the threaded holes (40) are spaced circumferentially along the crankshaft (31) on the stationary scroll plate (32), and at least five of the through holes (50) are spaced circumferentially along the crankshaft (31) on the bracket (34); or, At least five of the threaded holes (40) are spaced apart circumferentially along the crankshaft (31) on the bracket (34), and at least five of the through holes (50) are spaced apart circumferentially along the crankshaft (31) on the stationary scroll plate (32).

18. The compressor for use in an air conditioning system according to claim 1, characterized in that, The stationary scroll plate (32) has an exhaust port (323) that connects the accommodating cavity (101) and the compression cavity (301). The stationary scroll plate (32) is located on the side of the moving scroll plate (33) near the motor (20), and the bracket (34) is located on the side of the moving scroll plate (33) away from the motor (20).

19. The compressor for use in an air conditioning system according to claim 1, characterized in that, The refrigerant includes R32 refrigerant or R290 refrigerant; When the refrigerant includes R32 refrigerant, the compressor displacement V1 satisfies the following relationship: 8cm 3 ≤V1≤12cm 3 ;or, When the refrigerant includes R290 refrigerant, the compressor displacement V2 satisfies the following relationship: 16cm 3 ≤V2≤24cm 3 .

20. The compressor for use in an air conditioning system according to claim 1, characterized in that, The compressor also includes a liquid reservoir (60), and the housing (10) has an air inlet (11) and an air outlet (12). The air inlet (11) is connected to the liquid reservoir (60) and the compression chamber (301), and the air outlet (12) is connected to the accommodating chamber (101) and the outside. The liquid storage volume V3 of the liquid reservoir (60) satisfies the relationship 300mL≤V3≤500mL.

21. The compressor for use in an air conditioning system according to claim 1, characterized in that, The anti-rotation device (35) includes a cross slip ring, which is installed between the moving scroll plate (33) and the bracket (34); and / or, The housing (10) is provided with wiring terminals (70) for connecting the motor (20) and an external power supply.

22. 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 21.

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