Compressor applied to air conditioning system and air conditioning system

Abstract

The utility model discloses a kind of compressor and air conditioning system applied to air conditioning system. The compressor includes casing, motor and pump body assembly. Casing has accommodating cavity, motor is set in accommodating cavity. Pump body assembly is set in accommodating cavity and is set closer to the bottom of accommodating cavity than motor, pump body assembly includes crankshaft, static scroll, dynamic scroll and support, crankshaft is rotatably set in accommodating cavity, static scroll is close to the side of dynamic scroll and is provided with first scroll, dynamic scroll is provided with second scroll and is engaged with first scroll, and first scroll and second scroll are engaged to form compression chamber. The maximum circumferential diameter D1 of the outer diameter outside of dynamic scroll satisfies the relationship formula: 78mm≤D1≤90mm;The minimum distance S1 of the top surface end surface distance between the side of second scroll away from the center of eccentric bearing hole and first bearing hole satisfies the relationship formula: 0.8mm≤S1≤1.5mm. The present application solves the problem that the compressor is difficult to realize miniaturization.

Description

Technical Field

[0001] This utility model 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. The compressor is the core component of an air conditioner, and its energy efficiency significantly impacts the overall energy efficiency of the air conditioner. Therefore, air conditioner manufacturers are setting increasingly stringent energy efficiency requirements for compressors. 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.

[0003] Currently, leakage loss is one of the most significant losses in scroll compressors. Reducing leakage during the compression process of a scroll compressor pump can significantly improve its energy efficiency. Common methods to reduce leakage loss and improve compressor energy efficiency include increasing eccentricity, increasing wall thickness, and increasing the number of scroll turns. However, these methods not only increase the outer diameter of the moving and stationary discs but also further increase the overall size of the compressor, making it difficult to achieve compressor miniaturization and resulting in lower cost-effectiveness. Utility Model Content

[0004] The main objective of this invention is to provide a compressor and air conditioning system for use in air conditioning systems, so as to at least solve the problems of increased compressor size and low cost-effectiveness in the prior art due to the need to reduce leakage losses in scroll compressors.

[0005] According to one aspect of this utility model, a compressor for use in an air conditioning system is provided, wherein the displacement V of the compressor satisfies the relationship: 6cm 3 ≤V≤10cm 3 The compressor includes a vertical variable frequency scroll compressor, and the compressor further includes:

[0006] The housing has a receiving cavity, and the bottom of the receiving cavity is provided with an oil storage cavity 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 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, and a bracket. The crankshaft is rotatably disposed within the accommodating cavity. A first scroll plate is disposed on the side of the stationary scroll plate near the moving scroll plate. A second scroll plate is disposed on the moving scroll plate and meshes with the first scroll plate. The first scroll plate and the second scroll plate 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 section, an eccentric section, and a second shaft section. The first shaft section, the eccentric section, and the second shaft section are arranged sequentially along the axial direction of the crankshaft. The first shaft section mates with the first bearing hole or the second bearing hole. The second shaft section mates with the second bearing hole or the first bearing hole. The motor is sleeved on the first shaft section. The moving scroll plate is sleeved on the eccentric section through the eccentric bearing hole.

[0010] The maximum circumferential diameter D1 of the outer side of the moving scroll disk satisfies the following relationship: 78mm≤D1≤90mm;

[0011] The minimum top surface distance S1 between the side of the second vortex away from the center of the eccentric bearing hole and the first bearing hole satisfies the following relationship: 0.8mm≤S1≤1.5mm.

[0012] Furthermore, the minimum top surface distance S1 between the side of the second vortex away from the center of the eccentric bearing hole and the first bearing hole satisfies the following relationship: 0.8mm≤S1≤1.2mm.

[0013] Furthermore, the minimum distance S2 between the outer edges of the first vortex and the moving vortex disk satisfies the following relationship: 0.3mm≤S2≤1.5mm.

[0014] Furthermore, the diameter D2 of the eccentric bearing hole satisfies the following relationship: 14mm≤D2≤18mm.

[0015] Furthermore, the diameter D3 of the first bearing hole satisfies the following relationship: 11mm≤D3≤15mm.

[0016] Furthermore, the vortex profile of the second vortex includes an involute of a circle.

[0017] Furthermore, the eccentricity C of the eccentric segment satisfies the following relationship: C≥2mm.

[0018] 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.

[0019] 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.

[0020] According to another aspect of the present invention, an air conditioning system is provided, the air conditioning system including the compressor described above for use in air conditioning systems.

[0021] In this invention, since the stationary scroll 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 accommodating 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 accommodating 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, since the compressor in this application is a vertical scroll compressor, during operation, the moving scroll meshes with the stationary scroll and moves around the moving scroll to achieve volume changes in the compressor's compression cavity. During this process, the moving scroll needs to seal the stationary scroll, and the outer diameter of the moving scroll needs to be large enough to ensure a seal on the compression cavity. Therefore, by setting the compressor's D1 to satisfy the relationship 78mm≤D1≤90mm, it is possible to avoid the situation where the compressor's energy efficiency decreases due to an excessively small outer diameter of the moving scroll, and also to prevent the compressor's size from increasing due to an excessively large outer diameter of the moving scroll. This allows for compressor miniaturization and improves the compressor's cost-effectiveness. Furthermore, if the minimum sealing distance between the second scroll and the first bearing hole is too small, it will cause the compression chamber near the crankshaft to connect with the lubricating oil passage on the crankshaft when the second scroll meshes with the first scroll. This would allow lubricating oil from the crankshaft to enter the compression chamber, and gas from the working chamber might also enter the oil passage. If the minimum sealing distance between the second scroll and the first bearing hole is too large, it will increase the outer diameter of both the moving and stationary scrolls, further increasing the compressor's size. Therefore, setting the minimum sealing distance S1 between the top end face of the second scroll and the first bearing hole to satisfy the relationship 0.8mm≤S1≤1.5mm not only reduces the compressor's size and production cost, enabling miniaturization, but also reduces energy consumption and improves operational reliability. Attached Figure Description

[0022] The accompanying drawings, which are included to provide a further understanding of the present invention and constitute a part of this invention, illustrate exemplary embodiments of the present invention and, together with the description thereof, serve to explain the present invention and do not constitute an undue limitation thereof. In the drawings:

[0023] Figure 1This is a cross-sectional view of a compressor used in an air conditioning system, as disclosed in an embodiment of this utility model.

[0024] Figure 2 This is an exploded view of the pump body assembly disclosed in an embodiment of the present utility model;

[0025] Figure 3 This is a schematic diagram of the crankshaft structure disclosed in an embodiment of the present utility model;

[0026] Figure 4 This is a schematic diagram of the structure of the first and second vortexes in this embodiment when they are engaged, viewed from a first perspective.

[0027] Figure 5 This is a perspective view of the first and second vortexes in this embodiment when they are engaged, viewed from a second perspective.

[0028] Figure 6 This is a schematic diagram of the structure of the first and second vortexes in this embodiment when they are engaged and viewed from a second perspective.

[0029] The above figures include the following reference numerals:

[0030] 10. Housing; 101. Receptacle; 102. Oil reservoir; 20. Motor; 21. Rotor; 22. Stator; 30. Pump body assembly; 301. Compression chamber; 31. Crankshaft; 311. First shaft section; 312. Eccentric section; 313. Second shaft section; 32. Stationary scroll plate; 321. First scroll; 322. First bearing section; 323. First bearing hole; 33. Moving scroll plate; 331. Second scroll; 332. Eccentric bearing hole; 34. Bracket; 341. Second bearing section; 342. Second bearing hole; 40. Threaded hole; 50. Through hole. Detailed Implementation

[0031] It should be noted that, where there is no conflict, the embodiments and features in the embodiments of this utility model can be combined with each other. The present utility model will now be described in detail with reference to the accompanying drawings and embodiments.

[0032] 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 the present invention. 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.

[0033] 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 invention. 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.

[0034] See Figures 1 to 6 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 displacement V of the compressor satisfies the following relationship: 6cm 3 ≤V≤10cm 3 The compressor includes a vertical variable frequency scroll compressor for compressing a low-temperature, low-pressure refrigerant to obtain a high-temperature, high-pressure refrigerant. The compressor also includes a casing 10, a motor 20, and a pump assembly 30. Exemplarily, the displacement V of the compressor in this embodiment can be set to 6 cm³. 3 7cm 3 7cm 3 9cm 3 10cm 3 wait.

[0035] Specifically, the housing 10 has a receiving cavity 101, and the bottom of the receiving cavity 101 is provided with an oil storage cavity 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, and a bracket 34. The crankshaft 31 is rotatably disposed in the receiving cavity 101. The stationary scroll 32 is provided with a first scroll 321 on the side near the moving scroll 33. The moving scroll 33 is provided with a second scroll 331 that meshes with the first scroll 321. The first scroll 321 and the second scroll 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 323. 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 342. 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 arranged sequentially along the axial direction of the crankshaft 31. The first shaft section 311 is fitted with the first bearing hole 323 or the second bearing hole 342, and the second shaft section 313 is fitted with the second bearing hole 342 or the first bearing hole 323. The motor 20 is sleeved on the first shaft section 311, and the moving scroll plate 33 is sleeved on the eccentric section 312 through the eccentric bearing hole 332. The maximum circumferential diameter D1 of the outer side of the moving scroll disk 33 satisfies the relationship: 78mm≤D1≤90mm; the minimum distance S1 between the top end face of the second scroll 331 away from the center of the eccentric bearing hole 332 and the first bearing hole 323 satisfies the relationship: 0.8mm≤S1≤1.5mm.

[0036] It is understood that in this embodiment, the first shaft segment 311 may be engaged with the first bearing hole 323 and the second shaft segment 313 may be engaged with the second bearing hole 342, or the first shaft segment 311 may be engaged with the second bearing hole 342 and the second shaft segment 313 may be engaged with the first bearing hole 323.

[0037] In this embodiment, during the actual fabrication of the compressor, both the motor 20 and the pump assembly 30 can be installed within the accommodating cavity 101, with the first shaft segment 311 located on the side of the eccentric segment 312 closer to the motor 20, and the second shaft segment 313 located on the side of the eccentric segment 312 farther from the motor 20. The motor 20 is driven to rotate on the first shaft segment 311 of the crankshaft 31. When the motor 20 drives the crankshaft 31 to rotate, it also drives the eccentric segment 312 to rotate. Since the moving scroll plate 33 is fitted onto the eccentric segment 312 through the eccentric bearing hole 332, the rotation of the eccentric segment 312 synchronously drives the moving scroll plate 33 to rotate. Since the first scroll 321 of the stationary scroll 32 and the second scroll 331 of the moving scroll 33 mesh to form a compression chamber 301, the rotation of the moving scroll 33 synchronously drives the stationary scroll 32 to rotate relative to the moving scroll 33, causing a change in the volume of the compression chamber 301. This compresses the refrigerant entering the compression chamber 301 from the outside, effectively improving the compressor's energy efficiency. Multiple compression chambers 301 are formed by the meshing of the first scroll 321 and the second scroll 331. The sealing between each compression chamber 301 is good, with minimal leakage, further improving the performance of refrigerant compression.

[0038] 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 accommodating cavity 101 than the motor 20, that is, the compressor adopts a bottom-mounted structure of the pump body assembly 30, the presence of the first bearing portion 322 and the second bearing portion 341 can support the crankshaft 31, so there is no need to set an additional bearing on the other side of the motor 20 to support the crankshaft 31. At the same time, the first bearing portion 322 and the second bearing portion 341 are closer to the lubricating oil at the bottom of the accommodating cavity 101, so there is no need to set an additional bushing to ensure the reliable operation of the compressor. The overall structure is simple, the manufacturing cost is low, and the cost performance is high.

[0039] Furthermore, since the compressor in this embodiment is a vertical scroll compressor, during the operation of the compressor, the second scroll 331 on the moving scroll 33 meshes with the first scroll 321 on the stationary scroll 32 and moves around the first scroll 321 under the drive of the eccentric section 312 of the crankshaft 31 to achieve a change in the volume of the compression chamber 301. During the change in the volume of the compression chamber 301, the moving scroll 33 seals the stationary scroll 32. The outer diameter of the moving scroll 33 needs to be large enough to seal the compression chamber 301. The outer diameter of the moving scroll 33 is related to the eccentric bearing hole 332, the scroll tooth thickness, the eccentricity of the eccentric section 312, the number of scroll turns, and the sealing distance (the sealing distance between the second scroll 331 and the first bearing hole 323). The smaller the aforementioned parameters, the smaller the outer diameter of the moving scroll 33. An excessively small diameter of the eccentric bearing bore 332 leads to excessive surface pressure on the eccentric section 312, reducing reliability. Insufficient scroll tooth thickness results in scroll deformation, increasing the risk of meshing friction or even breakage. Insufficient eccentricity of the eccentric section 312 leads to excessive surface pressure on the first shaft section 311 and the second shaft section 313 of the crankshaft 31, also reducing reliability. A small number of scroll turns makes it difficult to increase the compressor's internal volume ratio, leading to undercompression losses and reduced energy efficiency. A small sealing distance between the second scroll 331 and the first bearing bore 323 results in excessive compressor leakage and reduced energy efficiency. Therefore, limiting the minimum size of the compressor improves its reliability and energy efficiency. However, an excessively large radial dimension of the moving scroll 33 increases the size of the stationary scroll 32, the entire pump assembly 30, and the compressor itself, increasing production costs, reducing cost-effectiveness, and hindering compressor miniaturization. Therefore, while ensuring that the compressor displacement V satisfies the relationship 6cm 3 ≤V≤10cm 3 Under the premise of ensuring that the maximum circumferential diameter D1 of the outer side of the moving scroll disk 33 satisfies the relationship 78mm≤D1≤90mm, for example, D1 can be 78mm, 79mm, 80mm, 81mm, 82mm, 83mm, 84mm, 85mm, 86mm, 87mm, 88mm, 89mm, 90mm, etc., thereby improving the reliability and energy efficiency of the compressor, reducing the size of the compressor, and ensuring the miniaturization of the compressor.

[0040] Furthermore, during the operation of the moving scroll 33, the crankshaft 31 has lubricating oil channels between it and the first bearing hole 323 and the eccentric bearing hole 332 to lubricate the bearing pair. If the minimum distance S1 between the top surface of the second scroll 331 (away from the center of the eccentric bearing hole 332) and the top surface of the first bearing hole 323 is too small, the compression chamber 301 near the crankshaft 31 when the first scroll 321 and the second scroll 331 mesh will become connected to the lubricating oil channel on the crankshaft 31. This will cause the lubricating oil in the lubricating oil channel to enter the compression chamber 301, increasing the compression resistance and reducing the compressor's energy efficiency. Furthermore, the gas in the compression chamber 301 may also enter the lubricating oil channel, severely affecting the lubrication effect between the bearing pairs, increasing the compressor's energy consumption, and reducing the compressor's operational reliability. If the minimum distance S1 between the top surface of the second scroll 331 (away from the center of the eccentric bearing hole 332) and the top surface of the first bearing hole 323 is too large, the outer diameter of the moving scroll 33 will increase, leading to an increase in the compressor's manufacturing cost and size. Therefore, in this embodiment, the minimum distance S1 between the top end face of the second vortex 331 away from the center of the eccentric bearing hole 332 and the first bearing hole 323 satisfies the relationship 0.8mm≤S1≤1.5mm (e.g., ...). Figure 4 As shown in the figure, for example, S1 can be set to 0.8mm, 0.9mm, 1.0mm, 1.1mm, 1.2mm, 1.3mm, 1.4mm, 1.5mm, etc., so as to ensure the high reliability and low energy consumption of the compressor, and avoid increasing the size of the compressor, thereby improving the cost performance of the compressor.

[0041] Further, see Figure 3 The diagram shows the minimum distance S1 between the top surface of the second scroll 331 away from the center of the eccentric bearing hole 332 and the first bearing hole 323 in this embodiment. In this embodiment, the minimum distance S1 between the top surface of the second scroll 331 away from the center of the eccentric bearing hole 332 and the first bearing hole 323 satisfies the relationship 0.8mm ≤ S1 ≤ 1.2mm. For example, S1 can be set to 0.8mm, 0.9mm, 1.0mm, 1.1mm, 1.2mm, etc. When S1 is less than 0.8mm, on the one hand, the compression chamber 301 near the crankshaft 31 when the first scroll 321 and the second scroll 331 mesh easily connects with the lubricating oil passage on the crankshaft 31, allowing lubricating oil in the lubricating oil passage to enter the compression chamber 301, increasing the compression resistance in the compression chamber 301 and reducing the compressor's energy efficiency. On the other hand, gas in the compression chamber 301 may also enter the lubricating oil passage, affecting the lubrication effect between the bearing pairs, increasing the compressor's energy consumption, and reducing the compressor's operational reliability. When S1 is greater than 1.2mm, the outer diameter of the moving scroll plate 33 will increase, leading to an increase in the manufacturing cost and size of the compressor, making it impossible to achieve compressor miniaturization and resulting in a lower cost-performance ratio.

[0042] Furthermore, in this embodiment, the minimum distance S2 between the outer edges of the first vortex 321 and the moving vortex disk 33 satisfies the relationship 0.3mm≤S2≤1.5mm (e.g., Figure 5 (As shown). During the rotational translation of the moving scroll 33 relative to the stationary scroll 32, the first scroll 321 and the second scroll 331 mesh to compress the refrigerant gas. At this time, the moving scroll 33 and the stationary scroll 32 need to be in close contact to achieve a sealing effect. The minimum distance S2 between the outer edges of the first scroll 321 and the moving scroll 33 is the minimum sealing distance between the end faces of the moving scroll 33 and the stationary scroll 32. If the minimum sealing distance between the end faces of the moving scroll 33 and the stationary scroll 32 is too small, the space between the support 34 and the moving scroll 33 will be connected to the compression chamber 301, which can easily lead to fluid leakage, increase the energy consumption of the compressor, and affect the intake process of the compression chamber 301. If the minimum sealing distance between the end faces of the moving scroll 33 and the stationary scroll 32 is too small or too large, it will increase the outer diameter of the moving scroll 33, further increasing the size of the stationary scroll 32 and the compressor, increasing the production cost of the compressor, and making it impossible to achieve compressor miniaturization. Therefore, the minimum distance S2 between the outer edges of the first vortex 321 and the moving vortex disk 33 is set to satisfy the relationship 0.3mm≤S2≤1.5mm. For example, S2 can be set to 0.3mm, 0.4mm, 0.5mm, 0.6mm, 0.7mm, 0.8mm, 0.9mm, 1.0mm, 1.1mm, 1.2mm, 1.3mm, 1.4mm, 1.5mm, etc.

[0043] Specifically, when S2 is less than 0.3mm, the space between the bracket 34 and the moving scroll plate 33 communicates with the compression chamber 301, causing fluid leakage, such as leakage of high-pressure gas in the compression chamber 301, affecting the intake process of the compression chamber 301, resulting in a decrease in the compressor's compression efficiency and an increase in energy consumption. When S2 is greater than 1.5mm, the outer diameter of the moving scroll plate 33 increases, and at the same time, the outer diameter of the stationary scroll plate 32 and the overall size of the compressor also increase. This increases the amount of processing materials used in the compressor, raising processing costs, and the increased compressor size leads to limited installation space.

[0044] Furthermore, in this embodiment, the diameter D2 of the eccentric bearing hole 332 satisfies the relationship: 14mm ≤ D2 ≤ 18mm (e.g., Figure 2 (As shown), for example, D2 can be set to 14mm, 15mm, 16mm, 17mm, 18mm, etc.

[0045] Specifically, when the diameter D2 of the eccentric bearing hole 332 of the moving scroll 33 is less than 14mm, the surface pressure on the eccentric section 312 of the crankshaft 31 will be too large, leading to a decrease in the reliability of the compressor. The smaller the diameter of the eccentric bearing hole 332 of the moving scroll 33, the more the crankshaft 31's first shaft section 311 and second shaft section 313 must be designed to be smaller, assuming the eccentricity of the eccentric section 312 remains constant. Otherwise, the crankshaft 31 cannot be inserted into the eccentric bearing hole 332 of the moving scroll 33. This will result in a decrease in the reliability of either the first shaft section 311 or the second shaft section 313 of the crankshaft 31, a decrease in the rigidity of the crankshaft 31, and a tendency to generate noise during compressor operation. When the diameter D2 of the eccentric bearing hole 332 of the moving scroll 33 is greater than 18mm, the outer diameter of the moving scroll 33 will be too large, resulting in excessive material usage in the pump body, a decrease in the compressor's cost-effectiveness, and an increase in its size.

[0046] Furthermore, in this embodiment, the diameter D3 of the first bearing hole 323 satisfies the relationship: 11mm ≤ D3 ≤ 15mm (e.g., Figure 2 (As shown), for example, D3 can be set to 11mm, 12mm, 13mm, 14mm, 15mm, etc.

[0047] Specifically, when the diameter D3 of the first bearing bore 323 is greater than 15mm, the sealing distance between the second scroll 331 of the moving scroll 33 and the first bearing bore 323 will be reduced, causing the space on both sides of the seal to connect, thereby reducing the energy efficiency and reliability of the compressor. When the diameter D3 of the first bearing bore 323 is less than 11mm, the surface pressure of the bearing pair of the first bearing part 322 will be too high, greatly reducing the reliability of the compressor.

[0048] Furthermore, the vortex profile of the second vortex 331 includes an involute of a circle.

[0049] Specifically, the involute curve of a circle is used as the scroll profile for the second scroll 331, which can cooperate with the first scroll 321 to form a series of continuously changing 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 teeth based on the involute curve can precisely run along 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.

[0050] Furthermore, the eccentricity C of the eccentric segment 312 satisfies the relationship: C≥2mm, for example, C can be set to 2.1mm, 2.2mm, 2.3mm, 2.4mm, etc.

[0051] Specifically, if the eccentricity C is too small, the surface pressure on the eccentric section 312 of the crankshaft 31 will be too large, resulting in a decrease in the reliability of the compressor. When the eccentricity C is less than 2mm, on the one hand, the centrifugal force during the operation of the moving scroll 33 is small, which affects the sealing performance of the compression chamber 301 and causes gas leakage, reducing the efficiency of the compressor. On the other hand, it increases the load on the crankshaft 31, resulting in a decrease in the reliability of the crankshaft 31 and an increase in frictional power consumption.

[0052] Further, see Figure 2 as well as Figure 6 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 appendix 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.

[0053] 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.

[0054] 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 6 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.

[0055] 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.

[0056] On the other hand, this application also discloses an air conditioning system that includes the aforementioned compressor used in air conditioning systems. Therefore, this air conditioning system possesses all the technical effects of the aforementioned compressor used in air conditioning systems. Since the technical effects of the compressor used in air conditioning systems have already been described in detail above, they will not be repeated here.

[0057] 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.

[0058] 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 utility model.

[0059] The above are merely preferred embodiments of this utility model and are not intended to limit the scope of this utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A compressor for use in an air conditioning system, wherein the displacement V of the compressor satisfies the following relationship: 6cm 3 ≤V≤10cm 3 The compressor includes 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 cavity (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), and a bracket (34). The crankshaft (31) is rotatably disposed in the accommodating cavity (101). A first scroll (321) is disposed on the side of the stationary scroll plate (32) near the moving scroll plate (33). A second scroll (331) is disposed on the moving scroll plate (33) and meshes with the first scroll (321). The first scroll (321) and the second scroll (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 (323). 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 (342). 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 segment (311), the eccentric segment (312), and the second shaft segment (313) are arranged sequentially along the axial direction of the crankshaft (31). The first shaft segment (311) is engaged with the first bearing hole (323) or the second bearing hole (342), and the second shaft segment (313) is engaged with the second bearing hole (342) or the first bearing hole (323). The motor (20) is sleeved on the first shaft segment (311), and the moving scroll plate (33) is sleeved on the eccentric segment (312) through the eccentric bearing hole (332). The maximum circumferential diameter D1 of the outer side of the moving vortex disk (33) satisfies the following relationship: 78mm≤D1≤90mm; The minimum distance S1 between the top end face of the second vortex (331) away from the center of the eccentric bearing hole (332) and the first bearing hole (323) satisfies the following relationship: 0.8mm≤S1≤1.5mm.

2. The compressor for use in an air conditioning system according to claim 1, characterized in that, The minimum distance S1 between the top end face of the second vortex (331) away from the center of the eccentric bearing hole (332) and the first bearing hole (323) satisfies the following relationship: 0.8mm≤S1≤1.2mm.

3. The compressor for use in an air conditioning system according to claim 1, characterized in that, The minimum distance S2 between the outer edges of the first vortex (321) and the moving vortex disk (33) satisfies the following relationship: 0.3mm≤S2≤1.5mm.

4. The compressor for use in an air conditioning system according to claim 1, characterized in that, The diameter D2 of the eccentric bearing hole (332) satisfies the following relationship: 14mm≤D2≤18mm.

5. The compressor for use in an air conditioning system according to claim 1, characterized in that, The diameter D3 of the first bearing hole (323) satisfies the following relationship: 11mm≤D3≤15mm.

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

7. The compressor for use in an air conditioning system according to claim 1, characterized in that, The eccentricity C of the eccentric segment (312) satisfies the following relationship: C≥2mm.

8. 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).

9. The compressor for use in an air conditioning system according to claim 8, 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.

10. 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 9.

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