Compressor and air conditioning equipment

Abstract

The present invention relates to a compressor and an air-conditioning device. The compressor includes: a housing (12) having a first chamber (A) and a second chamber (B) therein; a stator (3) disposed in the first chamber (A), and the stator (3) is axially provided with a first through hole (32); a rotor (2) passing through the first through hole (32); and an axial bearing (10) disposed in the second chamber (B) for bearing the axial force received by the rotor (2); wherein, the first chamber (A) and the second chamber (B) are fluid-isolated. Such a structure can not only fully cool the motor, but also prevent the liquid refrigerant accumulated at the bottom of the first chamber during the cooling process of the motor from entering the second chamber, so as to avoid excessive liquid refrigerant from affecting the performance of the axial bearing, thereby enabling the axial bearing to effectively balance the axial force received by the rotor and improving the working stability of the rotor.

Description

Technical Field

[0001] The present invention relates to the technical field of air compression equipment, and particularly to a compressor and an air-conditioning device. Background Art

[0002] A centrifugal refrigeration compressor belongs to a high-speed compressor. The compressor rotor rotates at a high speed during operation and requires a reliable bearing to support the rotor. The bearings commonly used for conventional rotors mainly include rolling bearings, oil film bearings, and magnetic levitation bearings, while for air suspension compressors, gas is mainly used for support. Its working principle is that during the high-speed rotation of the rotor, an air film is automatically formed between the bearing and the rotor to support the rotor.

[0003] A related technology known to the inventor is to design the bearing cavity to communicate with the motor cavity to introduce the refrigerant in the motor cavity to the bearing cavity to supply gas for the operation of the gas bearing. Such a structure has the following problems: if the amount of refrigerant is too small, the motor will not be cooled sufficiently; if the amount of refrigerant is too large, there will be too much liquid refrigerant at the bottom of the motor cavity. As the amount of refrigerant increases, the bearing will be submerged by the liquid refrigerant, making it difficult for the gas bearing to form a stable air film and resulting in poor working stability of the rotor. Summary of the Invention

[0004] The object of the present invention is to provide a compressor and an air-conditioning device that can improve the working stability of the rotor in the compressor.

[0005] According to a first aspect of the present invention, a compressor is provided, comprising:

[0006] A housing having a first cavity and a second cavity provided therein;

[0007] A stator disposed in the first cavity, and the stator is provided with a first through hole along the axial direction;

[0008] A rotor passing through the first through hole; and

[0009] An axial bearing disposed in the second cavity for bearing the axial force received by the rotor;

[0010] Wherein, the first cavity and the second cavity are fluid-isolated.

[0011] In some embodiments, the housing is provided with a first liquid discharge port and a second liquid discharge port, the first liquid discharge port communicates with the first cavity, and the second liquid discharge port communicates with the second cavity.

[0012] In some embodiments, the compressor further comprises:

[0013] A radial bearing disposed axially between the axial bearing and the stator;

[0014] A support member for supporting a rotor through a radial bearing, the support member being connected to a housing, and a first chamber being formed between one side of the support member and the housing, and a second chamber being formed between the other side of the support member and the housing.

[0015] In some embodiments, the compressor further includes:

[0016] A radial bearing axially disposed between the axial bearing and the stator for supporting the rotor; and

[0017] A seal sleeved on the rotor and located on the side of the radial bearing axially close to the stator, the seal being configured to be sealed with the rotor.

[0018] In some embodiments, the seal is axially provided with a second through hole, and a plurality of grooves are axially spaced on the side wall of the second through hole.

[0019] In some embodiments, the compressor further includes:

[0020] A support member connected to the housing for supporting the rotor through a radial bearing;

[0021] A diffuser; and

[0022] A thrust disk fixed to the rotor and axially located between the diffuser and the support member, and an axial bearing is provided on at least one side of the thrust disk axially.

[0023] Wherein, a first chamber is enclosed between the housing, the rotor, the seal and the support member, and a second chamber is enclosed between the housing, the diffuser and the support member.

[0024] In some embodiments, the compressor further includes:

[0025] A support member connected to the housing for supporting the rotor through a radial bearing;

[0026] Wherein, the seal is fixed to the support member and is used for thrusting against the radial bearing.

[0027] In some embodiments, an annular groove is provided on the end face of the support member facing the stator, and the seal includes:

[0028] A first part abutting against the ends of the radial bearing and the support member; and

[0029] A second part having an annular structure, connected to one end of the first part axially away from the stator, and the inner side wall of the second part is matched with the radially inner side wall of the annular groove.

[0030] In some embodiments, the outer side wall of the second part is matched with the radially outer side wall of the annular groove.

[0031] In some embodiments, the seal includes:

[0032] The first part abuts against the end of the radial bearing; and

[0033] The third part, one end of the third part is connected to the first part, and the first part and the third part are sleeved on the rotor together, and the other end of the third part extends in the direction close to the stator.

[0034] According to the second aspect of the present invention, an air conditioning device is provided, including the compressor of the above embodiment.

[0035] Based on the above technical solution, in the compressor of the embodiment of the present invention, a first chamber and a second chamber are provided in the housing, the stator is provided in the first chamber, the axial bearing is provided in the second chamber, and the first chamber and the second chamber are fluid-isolated. When situations such as liquid carry-over during suction or insufficient gasification for motor cooling occur, this structure can prevent the liquid refrigerant accumulated at the bottom of the first chamber from entering the second chamber along with the gaseous refrigerant, so as to avoid excessive liquid refrigerant from affecting the performance of the axial bearing, thereby enabling the axial bearing to effectively balance the axial force received by the rotor and improving the working stability of the rotor. Description of the Drawings

[0036] The drawings described herein are used to provide a further understanding of the present invention, form a part of this application, and the schematic embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation to the present invention. In the drawings:

[0037] Figure 1 It is a schematic structural diagram of an embodiment of the compressor of the present invention;

[0038] Figure 2 It is a schematic structural diagram of another embodiment of the compressor of the present invention;

[0039] Figure 3 It is a schematic structural diagram of still another embodiment of the compressor of the present invention;

[0040] Figure 4 is Figure 1 The enlarged view of I.

[0041] Description of the Reference Numerals

[0042] 1. Compressor housing; 2. Rotor; 3. Stator; 4. Support member; 5. Radial bearing; 6. Primary diffuser; 6'. Secondary diffuser; 7. Impeller; 8. Seal; 9. Thrust disk; 10. Axial bearing;

[0043] 11. First volute; 12. Housing; 13. Second volute; 121. First liquid discharge port; 122. Second liquid discharge port; 123. Guide groove; 31. Hole; 32. First through hole; 41. Annular groove; 81. First part; 82. Second part; 83. Groove; 831. First side wall; 832. Second side wall; 84. Extension part; 85. Third part; 811. Second through hole; 91. Thrust part; 92. Connection part. Detailed implementation manners

[0044] The present invention will be described in detail below. In the following paragraphs, different aspects of the embodiments are defined in more detail. Each aspect so defined can be combined with any other one or more aspects, unless explicitly stated that they cannot be combined. In particular, any feature considered to be preferred or advantageous can be combined with one or more other features considered to be preferred or advantageous.

[0045] The terms "first", "second", etc. used in the present invention are only for convenience of description to distinguish different components with the same name, and do not indicate a sequence or primary-secondary relationship.

[0046] To facilitate the description of the improvement points of the present invention, first, taking a centrifugal compressor as an example, its overall structure will be described below. Of course, the compressor can also be a screw compressor or a piston compressor, etc.

[0047] As Figure 1 shown, taking a two-stage centrifugal compressor as an example, it includes a compressor housing 1, a rotor 2, and a stator 3. The rotor 2 and the stator 3 form an electric motor, which is arranged inside the compressor housing. The stator 3 is a rotating part, on which a winding is provided and is fixed to the compressor housing by a tight fit to make the rotor 2 rotate at a high speed by generating a magnetic field. A first through hole 31 is provided axially on the stator 3, and the rotor 2 is inserted into the first through hole 31. The stator 3 can be located in the middle area of the rotor 2 in the axial direction, and the rotor 2 and the stator 3 are in clearance fit.

[0048] The compressor housing 1 is an irregular cavity part, which can be formed by casting, and mainly plays a role in supporting and fixing the stator 3 and the bearing housing. The compressor housing 1 can include: a first volute 11, a housing 12, and a second volute 13. The first volute 11 and the second volute 13 are respectively arranged at both ends of the housing 12 in the axial direction. The stator 3 is in tight fit with the housing 12. The housing 12 can be in a cylindrical structure. The rotor 2 is arranged at the central position of the housing 12. An impeller 7 is provided at each end of the rotor 2, and a diffuser is provided at the inner end of the impeller 7. When the impeller 7 rotates at a high speed, the gas rotates along with it. Under the action of centrifugal force, the gas is thrown into the rear diffuser for pressure increase, converting the velocity energy of the medium at the outlet of the impeller 7 into pressure energy, and the gas with increased pressure is discharged from the volute.

[0049] The diffuser includes a first-stage diffuser 6 and a second-stage diffuser 6'. The working principle of this two-stage centrifugal compressor is as follows: During the operation of the compressor, the rotor 2 rotates at a high speed. The gas enters the first-stage diffuser 6 through the impeller 7 on the left side. After being compressed at the first stage, the gas enters the first volute 11. The exhaust passage on the first volute 11 guides the compressed gas into the impeller on the right side. After the centrifugal action of the impeller 7 on the right side, the gas enters the second-stage diffuser 6'. After being compressed at the second stage, the gas enters the second volute 13 and is discharged from the compressor through the exhaust passage on the second volute 13.

[0050] On this basis, as Figure 1 shown, a first chamber A and a second chamber B are provided inside the housing 12. The stator 3 is arranged in the first chamber A, and the stator 3 is axially provided with a first through hole 32. The rotor 2 is inserted into the first through hole 32. The first chamber A is the motor chamber mentioned above. Since the impeller 7 does work on the refrigerant during operation, the outlet pressure is greater than the inlet pressure, and this pressure difference will generate an axial force. The compressor may further include an axial bearing 10 located in the second chamber B for bearing the axial force received by the rotor 2. The second chamber B serves as the bearing chamber of the axial bearing 10. For example, the axial bearing 10 can be a gas bearing, a magnetic levitation bearing, or a rolling thrust bearing, etc. Among them, the first chamber A and the second chamber B are fluid-isolated.

[0051] Most centrifugal compressors use evaporative or liquid injection cooling for the motor. In order to cool the stator 3 during the operation of the compressor, a spiral guide groove 123 is provided on the inner side wall of the housing 12 to guide the refrigerant from the first chamber A on the first side of the stator 3 to the first chamber A on the second side, so as to cool the stator 3 during the flow process. The gaseous refrigerant formed after cooling the stator 3 returns from the gap between the stator 3 and the rotor 2 to cool the rotor 2. The liquid refrigerant that has not been completely vaporized after cooling the stator 3 can return to the first chamber A on the first side through the hole 31 axially provided on the stator 3.

[0052] If the amount of refrigerant is too small, it will cause insufficient cooling of the motor. In order to ensure sufficient cooling of the motor, a sufficient amount of refrigerant needs to be introduced, which may accumulate liquid refrigerant at the bottom of the first chamber A. Since the first chamber A and the second chamber B are fluid-isolated, it can prevent the liquid refrigerant in the first chamber A from entering the second chamber B, so as to avoid excessive liquid refrigerant affecting the performance of the axial bearing, so that the axial bearing can effectively balance the axial force received by the rotor and improve the stability of the rotor operation. In this way, it can not only solve the problem of high operating temperature of the motor, but also prevent the liquid refrigerant that has not been vaporized after cooling the motor from affecting the working performance of the axial bearing 10.

[0053] For example, the axial bearing 10 includes an axial gas bearing, which can be a hydrostatic gas bearing or a hydrodynamic gas bearing. When the axial gas bearing is immersed in the liquid refrigerant, it is difficult to form a stable gas film in the working gap, resulting in collision and friction between the rotor 2 and the axial bearing 10. By fluid-isolating the first chamber A and the second chamber B, and arranging the stator 3 and the axial bearing 10 in the first chamber A and the second chamber B respectively, it is possible to prevent the liquid refrigerant in the first chamber A from immersing the axial gas bearing, form a stable gas film in the working gap, effectively balance the axial force received by the rotor, and improve the working stability of the rotor.

[0054] When the axial bearing 10 includes a hydrodynamic gas bearing, since the first chamber A and the second chamber B are fluid-isolated, it is difficult to introduce the gaseous refrigerant in the first chamber A into the second chamber B to supply gas to the axial bearing 10. At this time, the gas supply of the axial bearing 10 mainly comes from the gas leaking from the gap between the upstream components of the axial bearing 10.

[0055] The components upstream of the axial bearing 10 are mainly diffusers. Since the gas is slightly hotter due to being compressed by the impeller 7 at this location and fills the second chamber B, it can ensure that the axial bearing 10 operates at a suitable temperature. Since the leaked gas needs to bear the axial force received during the operation of the rotor 2, it will cause the gas temperature to further increase, which can vaporize a small amount of liquid refrigerant leaked from the first chamber A into the second chamber B through the installation gap between the supporting component 4 and the housing 12, thereby consuming the heat of its own gas and stabilizing the temperature in the entire second chamber B at the working temperature required by the axial bearing 10.

[0056] As Figure 1 shown, the housing 12 is provided with a first liquid drain port 121 and a second liquid drain port 122. The first liquid drain port 121 is communicated with the first chamber A for discharging the liquid refrigerant in the first chamber A; the second liquid drain port 122 is communicated with the second chamber B for discharging the liquid refrigerant in the second chamber B. The discharged liquid refrigerant can be supplemented to the evaporator with a lower pressure.

[0057] This structure can timely discharge the liquid refrigerant in the first chamber A and the second chamber B, prevent a large amount of liquid refrigerant from accumulating in the first chamber A, so as to avoid the resistance formed by the rotor 2 stirring the liquid during rotation, prevent the liquid refrigerant in the first chamber A from entering the second chamber B through the mating gap between parts and affecting the working performance of the axial bearing 10, and prevent a large amount of liquid refrigerant from accumulating in the second chamber B and affecting the working performance of the axial bearing 10. Moreover, when the compressor is used in air-conditioning equipment, the utilization rate of the refrigerant can be improved. In the prior art, only one liquid drain port is provided.

[0058] Preferably, the first liquid discharge port 121 is arranged in the area of the housing 12 corresponding to the first chamber A, and the second liquid discharge port 122 is arranged in the area of the housing 12 corresponding to the second chamber B, which can simplify the structure of the liquid discharge port. Optionally, the first liquid discharge port 121 and the second liquid discharge port 122 can also be arranged at any position on the housing 12, and the first liquid discharge port 121 and the second liquid discharge port 122 are respectively communicated with the first chamber A and the second chamber B by arranging a drainage channel in the housing 12.

[0059] As Figure 1 shown, the compressor of the present invention may further include a radial bearing 5 and a support member. Among them, the radial bearing 5 is arranged axially between the axial bearing 10 and the stator 3 for supporting the rotor 2. For example, radial bearings are respectively arranged at both ends of the rotor 2. The support member 4 is used to support the rotor 2 through the radial bearing 5. The support member 4 is connected to the housing 12, and a first chamber A is formed between one side of the support member 4 and the housing 12, and a second chamber B is formed between the other side of the support member 4 and the housing 12. For example, the radial bearing 5 can be a gas bearing, a magnetic levitation bearing or a rolling thrust bearing, etc.

[0060] By arranging the support member 4, not only can the radial bearing 5 be supported, but also it is convenient to divide the space in the housing 12 into the first chamber A and the second chamber B through the connection between the support member 4 and the housing 12. The structure is simple, and it is also beneficial to improve the fluid isolation degree between the first chamber A and the second chamber B.

[0061] For example, the radial bearing 5 includes a radial gas bearing, which can be a hydrostatic gas bearing or a hydrodynamic gas bearing. For example, the working principle of the hydrodynamic gas bearing is to utilize the high-speed rotating rotor 2 to form a supporting gas film with stiffness in the wedge-shaped area between the radial bearing 5 and the rotor 2. When the radial gas bearing is immersed in the liquid refrigerant in the first chamber A, it is difficult to form a stable gas film in the working gap, resulting in collision and friction between the rotor 2 and the radial bearing 5. For this reason, the compressor of the present invention may further include a seal 8, which is sleeved on the rotor 2 and is located on the side of the radial bearing 5 close to the stator 3 along the axis. The seal 8 is configured to be sealed with the rotor 2, that is, a dynamic seal is formed between the seal 8 and the rotor 2. For example, the seal 8 can be made of rubber or fluoroplastics, etc.

[0062] The air supply of the radial bearing 5 mainly comes from two parts: one is the gas leaked from the gap of the second chamber B, which is the main source; the other is the gas formed when cooling the motor in the first chamber A, and the gas can reach the radial bearing 5 through the gap between the seal 8 and the rotor 2.

[0063] When the gaseous refrigerant in the first chamber A reaches the radial bearing through the gap between the seal 8 and the rotor 2, the liquid refrigerant mixed in the gaseous refrigerant can be removed as much as possible, preventing the liquid refrigerant that has not vaporized during the motor cooling process in the first chamber A from submerging the radial bearing 5. A stable gas film can be formed in the working gap between the radial bearing 5 and the rotor 2, thereby improving the working stability of the rotor 2 and enhancing the load-bearing capacity of the radial bearing 5 for the rotor 2, and preventing collision and friction between the rotor 2 and the axial bearing 10. In addition, it can also prevent solid impurities in the first chamber A from entering the working gap of the radial bearing 5, improving the working reliability and service life of the radial bearing 5.

[0064] When the gas in the first chamber A reaches the radial bearing 5 through the gap between the seal 8 and the rotor 2, a small amount of liquid refrigerant will also remain. When passing through the seal 8 and entering the radial bearing 5, it will throttle and cool down, and mix with the high-temperature gas leaked from the second chamber B, which can maintain the temperature required for the radial bearing 5 to work, vaporize the liquid refrigerant in the radial bearing 5, and form a stable working gas film for the radial bearing.

[0065] As Figure 4 shown, the seal 8 is provided with a second through hole 811 along the axial direction. A plurality of grooves 83 are arranged at intervals along the axial direction on the side wall of the second through hole 811, forming a comb-tooth seal structure, which can reduce the liquid refrigerant in the first chamber A from entering the working gap of the radial bearing through the gap between the seal 8 and the rotor 2. Specifically, the groove 83 can be trapezoidal. The first side wall 831 of the groove 83 is an inclined surface, and the second side wall 832 is perpendicular to the axis of the rotor 2. This structure can further increase the sealing performance between the seal 8 and the rotor 2, and form a stable gas film in the working gap between the radial bearing 5 and the rotor 2.

[0066] As Figure 1 shown, the compressor of the present invention is a centrifugal compressor, and further includes: a diffuser, connected to the housing 12; and a thrust disk 9, fixed to the rotor 2 and axially located between the diffuser and the support member 4. The thrust disk 9 includes a thrust portion 91 and a connecting portion 92 connected axially. Axial bearings 10 are provided on at least one side of the thrust portion 91 along the axial direction, and there is an axial working gap between the axial bearing 10 and the thrust portion 91. A third through hole is provided on the diffuser, and the connecting portion 92 passes through the third through hole.

[0067] In Figure 1 it, both axial bearings 10 are located at one end of the rotor 2. One axial bearing 10 is fixed to one end of the first-stage diffuser 6 facing the thrust portion 91, and the other axial bearing 10 is fixed to one end of the support member 4 facing the thrust portion 91.

[0068] In this structure, the axial bearing 10 is arranged at one end of the rotor 2. Only a thrust disc 9 and an axial bearing 10 need to be arranged at one end of the rotor 2, which can shorten the axial length of the compressor and simplify the internal structure of the compressor. Moreover, since the direction of the axial force received by the rotor 2 during operation is uncertain, an axial bearing 10 is arranged on each side of the thrust portion 91, which can simultaneously bear the axial forces in two directions received by the rotor 2, prevent the rotor 2 from having an axial offset load, ensure the stable and reliable operation of the compressor under all working conditions and during reverse rotation, and improve the service life of the axial bearing in the compressor. Herein, the operating conditions of the compressor refer to the evaporation temperature and the condensation temperature of the system where the compressor is located. All working conditions mean that the compressor operates within a certain evaporation temperature range and a certain condensation temperature range. When the compressor stops, since the exhaust pressure is higher than the suction pressure, a reverse rotation situation will occur after shutdown.

[0069] Optionally, an axial bearing 10 is arranged at each end of the rotor 2 to respectively bear the axial forces in two directions received by the rotor 2. This structure requires thrust discs 9 to be arranged at both ends of the rotor 2.

[0070] On the basis of this embodiment, a first chamber A is formed by enclosing between the housing 12, the rotor 2, the seal 8 and the support member 4, and the stator 3 is arranged in the first chamber A; a second chamber B is formed by enclosing between the housing 12, the diffuser and the support member 4, and the axial bearing 10 is arranged in the second chamber B.

[0071] As Figure 1 shown, the compressor of the present invention may further include: a support member 4, connected to the housing 12, and used to support the rotor 2 through a radial bearing 5; wherein, the seal 8 is fixed to the support member 4 and is used to thrust against the radial bearing 5. For example, the seal 8 can abut against the end faces of the radial bearing 5 and the support member 4 close to the stator 3 and be fixed by fasteners or the like, or the seal 8 can also be fixed to the support member 4 by a tight fit. This structure can firmly fix the seal 8, improve the sealing effect, and can reliably limit the position of the radial bearing 5.

[0072] Specifically, as Figure 1 shown, an annular groove 41 is provided on the end face of the support member 4 facing the stator 3, which can reduce the weight of the support member 4. The seal 8 includes: a first portion 81, abutting against the ends of the radial bearing 5 and the support member 4; and a second portion 82, having an annular structure, connected to one end of the first portion 81 axially away from the stator 3, and the inner side wall of the second portion 82 is matched with the radially inner side wall of the annular groove 41.

[0073] In this structure, the part of the supporting member 4 located radially inside the annular groove 41 is embedded in the annular second part 82, which can circumferentially position the seal 8 to maintain a uniform sealing gap everywhere in the circumferential direction and optimize the sealing effect. Moreover, the seal 8 can be more reliably fixed to the supporting member 4 to prevent the seal 8 from shaking during the operation of the rotor.

[0074] In Figure 1 the structure shown, there is a gap between the outer sidewall of the second part 82 and the radially outer sidewall of the annular groove 41. This structure can reduce the volume of the seal 8.

[0075] In Figure 2 the structure shown, the outer sidewall of the second part 82 cooperates with the radially outer sidewall of the annular groove 41. This structure can make the seal 8 fit into the annular groove 41 for easy positioning and can also close the annular groove 41 to improve the refrigerant utilization rate. Or further, as in Figure 2 the seal 8 on the right side of the rotor 2 in, an extension 84 is provided at one end of the second part 82 close to the stator 3, and the extension 84 can extend radially outward to abut against the inner sidewall of the housing 12 to obtain a better positioning effect.

[0076] As Figure 3 shown, in order to further improve the sealing effect, the seal 8 includes: a first part 81 that abuts against the ends of the radial bearing 5 and the supporting member 4; and a third part 85, one end of the third part 85 is connected to the first part 81 and is sleeved on the rotor 2 together with the first part 81, and the other end of the third part 85 extends in the direction close to the stator 3. Similar to Figure 1 the same, the second part 82 can also be provided.

[0077] This structure can extend the sealing path between the seal 8 and the rotor 2, thereby optimizing the sealing effect. Moreover, it can also make the seal 8 contact the rotor 2 more stably and prevent the seal 8 from tilting. For example, grooves 83 can be axially spaced at intervals along the entire corresponding length section of the first part 81 and the third part 85 to form a comb tooth seal structure.

[0078] In the above embodiments, a radial bearing 5 is provided at each end of the rotor 2, and each radial bearing 5 is connected to the housing 12 through a supporting member 4. For the convenience of processing, the housing 12 and the two supporting members 4 can be designed in a split manner. When the production volume is small, the housing 12 and the supporting members 4 can be directly machined by a machine tool, saving the casting cost. Moreover, it is beneficial to the assembly of the stator 3 and the radial bearing 5 and can prevent scratches on the mating surfaces when axially loading parts.

[0079] Secondly, the present invention also provides an air conditioning device, which includes a refrigeration cycle system, and the refrigerant in the compressor is sourced from the refrigerant in the refrigeration cycle system. The air conditioning device includes a refrigeration cycle system formed by a condenser, an evaporator, and a compressor.

[0080] The above has introduced in detail a compressor and an air conditioning device provided by the present invention. Specific embodiments are used herein to elaborate on the principle and implementation manner of the present invention. The description of the above embodiments is only used to help understand the method and its core idea of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the principle of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the protection scope of the claims of the present invention.

Claims

1. A compressor, characterized in that, Comprising: A housing (12) having a first chamber (A) and a second chamber (B) provided therein; A stator (3) disposed in the first chamber (A), and the stator (3) having a first through-hole (32) provided axially therein; A rotor (2) passing through the first through-hole (32); and An axial bearing (10) disposed in the second chamber (B) for bearing the axial force exerted by the rotor (2); Wherein, the first chamber (A) and the second chamber (B) are fluid-isolated to prevent the liquid refrigerant in the first chamber (A) from entering the second chamber (B) and affecting the performance of the axial bearing (10), and the gas supply for the axial bearing (10) comes from the gas leaking from the gap between the upstream components of the axial bearing (10); The housing (12) is provided with a first drain port (121) and a second drain port (122), the first drain port (121) is in communication with the first chamber (A), and the second drain port (122) is in communication with the second chamber (B), and the discharged liquid refrigerant is replenished into the evaporator.

2. The compressor according to claim 1, characterized in that, Further comprising: A radial bearing (5) axially disposed between the axial bearing (10) and the stator (3); A support member (4) for supporting the rotor (2) through the radial bearing (5), the support member (4) is connected to the housing (12), and one side of the support member (4) and the housing (12) form the first chamber (A), and the other side of the support member (4) and the housing (12) form the second chamber (B).

3. The compressor according to claim 1, wherein Further comprising: A radial bearing (5) axially disposed between the axial bearing (10) and the stator (3) for supporting the rotor (2); And A seal (8) sleeved on the rotor (2) and located axially on the side of the radial bearing (5) close to the stator (3), and the seal (8) is configured to be sealed with the rotor (2).

4. The compressor according to claim 3, characterized in that, The seal (8) is axially provided with a second through-hole (811), and a plurality of grooves (83) are axially spaced on the side wall of the second through-hole (811).

5. The compressor according to claim 3, characterized in that, Further comprising: A support member (4) connected to the housing (12) for supporting the rotor (2) through the radial bearing (5); Diffusers (6, 6'); and A thrust disk (9) fixed to the rotor (2) and axially located between the diffusers (6, 6') and the support member (4), and at least one side of the thrust disk (9) in the axial direction is provided with the axial bearing (10); Wherein, a first chamber (A) is formed by enclosing between the housing (12), the rotor (2), the seal (8) and the support member (4), and a second chamber (B) is formed by enclosing between the housing (12), the diffusers (6, 6') and the support member (4).

6. The compressor according to claim 3, characterized in that, Further comprising: A support member (4) connected to the housing (12) for supporting the rotor (2) through the radial bearing (5); Among them, the seal (8) is fixed to the support member (4) and is used to thrust against the radial bearing (5).

7. The compressor according to claim 6, characterized in that, An annular groove (41) is provided on the end face of the support member (4) facing the stator (3). The seal (8) includes: A first part (81) that abuts against the end of the radial bearing (5) and the support member (4); and A second part (82) having an annular structure, which is connected to one end of the first part (81) axially away from the stator (3). The inner side wall of the second part (82) cooperates with the radially inner side wall of the annular groove (41).

8. The compressor according to claim 7, characterized in that, The outer side wall of the second part (82) cooperates with the radially outer side wall of the annular groove (41).

9. The compressor according to claim 3, characterized in that, The seal (8) includes: A first part (81) that abuts against the end of the radial bearing (5); and A third part (85), one end of the third part (85) is connected to the first part (81), and the first part (81) and the third part (85) are jointly sleeved on the rotor (2). The other end of the third part (85) extends in the direction close to the stator (3).

10. An air conditioning device, characterized in that, Including the compressor according to any one of claims 1 to 9.

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