Compressors and air conditioners

Abstract

The present invention relates to a compressor and an air conditioner. The compressor includes: a housing; a rotating shaft rotatably disposed in the housing; a bearing fixedly disposed in the housing, the bearing being provided with a first hole allowing the rotating shaft to pass through; and a sealing member fixedly disposed at the end of the bearing, the sealing member being provided with a second hole allowing the rotating shaft to pass through, the hole wall of the second hole being provided with at least one first groove. When a mixed refrigerant containing small particles of impurities and a small amount of residual liquid refrigerant passes through the first groove, the small particles of impurities with relatively large gravity and the liquid refrigerant are separated by gravity and enter the first groove, which can effectively prevent solid impurities and liquid refrigerant from entering between the rotating shaft and the bearing.

Description

Technical Field

[0001] The present invention relates to the field of compressors, and in particular to a compressor and an air conditioner. Background Art

[0002] Bearings are essential transmission components in modern mechanical equipment, primarily serving as supports. Based on their frictional properties, bearings can be categorized as rolling bearings, plain bearings, magnetic bearings, and air bearings. Air bearings offer a range of advantages, including low friction loss, virtually zero friction at extremely high speeds, excellent high-temperature stability, low vibration, and the absence of lubrication. Their application in high-speed turbines, such as centrifugal compressors, holds great promise.

[0003] Air bearings are divided into static gas bearings and dynamic gas bearings based on the different mechanisms for generating the lubricating gas film. Static gas bearings use an external gas source to supply air to the bearing to generate pressure to support the load. Dynamic gas bearings use the pressure gas film generated by gas in the wedge-shaped space between the shaft and the inner surface of the bearing to support the load. When the shaft rotates at high speed, it continuously introduces gas of a certain viscosity into the wedge-shaped gap. The continuous entry of gas causes the gas film to generate a certain pressure. When the gas film force is sufficient to balance the external load, a complete pressure lubricating gas film will be generated on the surfaces of the bearing and shaft, and the shaft and bearing will be completely separated, and friction will basically disappear. The damping of the dynamic bearing is generated by the mutual misalignment friction between the bearing housing, top foil, and elastic foil.

[0004] In summary, gas enters between the shaft and the bearing to form a pressure air film. However, when the related hydrodynamic bearing is working, there is a problem that impurities and excessive liquid are mixed between the shaft and the bearing, causing the pressure air film to be destroyed. Summary of the Invention

[0005] One of the objectives of the present invention is to provide a compressor and an air conditioner for alleviating the problem of impurities mixing between the shaft and the bearing.

[0006] Some embodiments of the present invention provide a compressor comprising:

[0007] case;

[0008] a rotating shaft rotatably disposed in the housing;

[0009] a bearing fixedly disposed in the housing, the bearing being provided with a first hole allowing the rotating shaft to pass through; and

[0010] A sealing member is fixedly arranged at the end of the bearing. The sealing member is provided with a second hole allowing the rotating shaft to pass through. The hole wall of the second hole is provided with at least one first groove.

[0011] In some embodiments, a first gap is formed between the hole wall of the first hole and the rotating shaft, and a second gap is formed between the hole wall of the second hole and the rotating shaft, and the second gap is smaller than or equal to the first gap.

[0012] In some embodiments, the at least one first groove includes a plurality of first annular grooves arranged around the axis of the rotating shaft, and annular teeth are formed between two adjacent first annular grooves to form a comb-teeth seal between the hole wall of the second hole and the rotating shaft.

[0013] In some embodiments, the at least one first groove comprises a spiral groove disposed about the axis of the rotating shaft.

[0014] In some embodiments, an axial dimension of a groove top of the first groove is greater than an axial dimension of a groove bottom, and the groove top of the first groove is closer to the rotating shaft than the groove bottom.

[0015] In some embodiments, the first groove includes a first side wall and a second side wall, the first side wall is close to the bearing relative to the second side wall, and the first side wall extends radially along the rotating shaft, and the section of the second side wall located at the top of the groove is farther away from the bearing than the section located at the bottom of the groove.

[0016] In some embodiments, the portion where the seal contacts and connects with the bearing is a side wall of the first groove.

[0017] In some embodiments, the seals are provided at both ends of the bearing along the axial direction of the rotating shaft.

[0018] In some embodiments, the seal includes a first annular portion and a second annular portion, the outer diameter of the first annular portion is larger than the outer diameter of the second annular portion, the first annular portion is fixedly connected to the bearing, the second annular portion is connected to the first annular portion, and the second annular portion extends along the axial direction of the rotating shaft away from the bearing.

[0019] In some embodiments, at least one second groove is provided on the rotating shaft near the sealing member, and the second groove is away from the bearing relative to the sealing member.

[0020] In some embodiments, a seal is provided at both ends of the bearing along the axial direction of the shaft, and at least one second groove is provided at a portion of the shaft close to the seal, and the second groove is away from the bearing relative to the seal.

[0021] In some embodiments, an axial dimension of a groove top of the second groove is greater than an axial dimension of a groove bottom, wherein the groove bottom of the second groove is closer to the central axis of the rotating shaft relative to the groove top.

[0022] In some embodiments, the second groove includes a third side wall and a fourth side wall, the third side wall is close to the bearing relative to the fourth side wall, and the third side wall extends radially along the rotating shaft, and the section of the fourth side wall located at the top of the groove is away from the bearing relative to the section located at the bottom of the groove.

[0023] In some embodiments, the at least one second groove includes a plurality of second annular grooves arranged around the axis of the rotating shaft or a spiral groove arranged around the axis of the rotating shaft.

[0024] Some embodiments of the present invention provide an air conditioner comprising the above-mentioned compressor.

[0025] Based on the above technical solution, the present invention has at least the following beneficial effects:

[0026] In some embodiments, the seal is fixed to the end of the bearing, and the seal is provided with a second hole allowing the rotating shaft to pass through. The hole wall of the second hole is provided with at least one first groove. When the mixed refrigerant mixed with small particle impurities and a small amount of residual liquid refrigerant passes through the first groove, the small particle impurities and liquid refrigerant with relatively large gravity are separated under the action of gravity and enter the first groove, which can effectively prevent solid impurities and liquid refrigerant from entering between the rotating shaft and the bearing. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] The drawings described herein are used to provide a further understanding of the present invention and constitute a part of this application. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0028] Figure 1 A partial cross-sectional schematic diagram of a compressor provided in some embodiments of the present invention;

[0029] Figure 2 for Figure 1 Enlarged schematic diagram of the middle part A.

[0030] Description of the reference numerals in the accompanying drawings:

[0031] 1-shell; 11-spiral flow channel; 12-refrigerant inlet; 13-refrigerant outlet;

[0032] 2-rotating shaft; 21-second slot;

[0033] 3-bearing; 31-elastic foil; 32-top foil;

[0034] 4-seal; 41-first groove; 411-first side wall; 42-first annular portion; 43-second annular portion;

[0035] 5-bearing support;

[0036] 6-motor stator; 61-first channel;

[0037] 7- Second channel;

[0038] 8-pneumatic chamber;

[0039] 91-first motor cavity; 92-second motor cavity. DETAILED DESCRIPTION

[0040] The following will be combined with the accompanying drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making any creative efforts are within the scope of protection of the present invention.

[0041] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the scope of protection of the present invention.

[0042] like Figure 1 As shown, the compressor includes a housing 1 , a rotating shaft 2 , a bearing 3 , a bearing support 5 and a motor stator 6 .

[0043] The cavity formed by the shell 1 is irregular in shape. The shell 1 is generally formed by casting and plays the role of supporting, protecting and shock absorbing.

[0044] Shaft 2 is a solid, shaft-like component and a crucial component of the motor. It is rotatably mounted within housing 1. During operation, shaft 2 rotates at high speed under the influence of an electromagnetic field. Shaft 2 is the motor rotor within the compressor.

[0045] The motor stator 6 is a rotating component and a crucial component of the motor, primarily composed of windings. It is located within and fixed to the housing 1. A first passage 61 is defined within the stator 6, located near the outer edge of the stator 6. The rotating shaft 2 passes through the stator 6, with a gap between them forming a second passage 7.

[0046] The rotating shaft 2 passes through the motor stator 6 . The rotating shaft 2 is provided with a bearing 3 at a position close to a first end of the motor stator 6 . The rotating shaft 2 is provided with another bearing 3 at a position close to a second end of the motor stator 6 .

[0047] The bearing support 5 is disposed within and connected to the housing 1. The bearing support 5 has a through-hole, into which the bearing 3 is fixedly mounted. The bearing 3 also has a through-hole through which the rotating shaft 2 passes. The bearing 3 comprises a bearing body, an elastic foil 31, and a top foil 32. The top foil 32 is positioned closer to the rotating shaft 2 than the elastic foil 31.

[0048] In order to achieve good coaxiality between the bearing 3 equipped with the elastic foil 31 and the top foil 32 and the rotating shaft 2, the housing 1, the bearing support 5 and the bearing 3 should be pre-assembled together, and then the through hole on the bearing 3 that allows the rotating shaft 2 to pass through should be bored; alternatively, the housing 1 and the bearing support 5 should be pre-assembled together, and then the through hole on the bearing support 5 that allows the rotating shaft 2 to pass through and can be set with the bearing 3 should be bored.

[0049] A first motor cavity 91 is formed between the first end of the motor stator 6 and the bearing 3 and the bearing support 5 provided at the end, and a second motor cavity 92 is formed between the second end of the motor stator 6 and the bearing 3 and the bearing support 5 provided at the end.

[0050] The inner wall of the housing 1 is provided with a spiral groove, which cooperates with the motor stator 6 to form a spiral flow channel 11. The side wall of the housing 1 is also provided with a refrigerant inlet 12 and a refrigerant outlet 13. The refrigerant inlet 12 is located near the second motor cavity 92, and the refrigerant outlet 13 is located on the side wall of the housing 1 corresponding to the second motor cavity 92.

[0051] During operation, refrigerant is introduced into the refrigerant inlet 12, enters the spiral flow channel 11, and flows within the spiral flow channel 11 to cool the motor. After cooling the motor, the refrigerant enters the first motor cavity 91 from the spiral flow channel 11. At this time, the refrigerant is partially vaporized and partially remains in liquid form. In the case of a pneumatic bearing 3, the refrigerant that absorbs heat and vaporizes enters the bearing 3, and the rest flows through the second channel 7 to the second motor cavity 92. The refrigerant outlet 13 is connected to the second motor cavity 92 and is also connected to the evaporator, so that the pressure in the second motor cavity 92 is lower than that in the first motor cavity 91, so that the gaseous refrigerant flows from the first motor cavity 91 to the second motor cavity 92 due to the pressure difference.

[0052] After heat exchange, the refrigerant that has not vaporized and remains in liquid form remains in the first motor cavity 91. To prevent liquid accumulation at the bottom of the first motor cavity 91 and the potential risk of liquid contamination in the bearing 3, a first channel 61 is provided inside the motor stator 6. The first channel 61 connects the first motor cavity 91 and the second motor cavity 92 at both ends of the motor stator 6. During operation, when the liquid level in the first motor cavity 91 reaches the pressure differential of the first channel 61, the liquid refrigerant in the first motor cavity 91 rapidly flows through the first channel 61 to the second motor cavity 92 and out through the refrigerant outlet 13.

[0053] The cavity between the bearing support 5 and the end of the bearing 3 away from the motor stator 6 forms the pneumatic cavity 8. This cavity is formed by the housing 1 and pneumatic components (such as the impeller and diffuser). It connects the hydrodynamic bearing and the pneumatic components and serves as one source of air for the hydrodynamic bearing. The first motor cavity 91 is another source of air for the hydrodynamic bearing.

[0054] Hydrodynamic bearings utilize a pressure film of gas created in the wedge-shaped space between the shaft and the inner surface of the bearing to support loads. As the shaft 2 rotates at high speed, it continuously draws gas of a certain viscosity into the space between the shaft 2 and the bearing 3. This continuous influx of gas creates a constant pressure in the air film. When the force of the air film is sufficient to balance the external load, a complete pressure-lubricated air film forms on the surfaces of the bearing 3 and the shaft 2, completely separating the shaft 2 and bearing 3, and friction is virtually eliminated.

[0055] Gas enters the space between the shaft 2 and the bearing 3, forming a pressure film. Due to the lack of a filtering device, gas impurities are mixed in between the shaft 2 and the bearing 3. Because the bearing 3 comprises an elastic foil structure, the special nature of the elastic foil structure allows for a small amount of impurities to enter. However, excessive impurities can cause scratches at best, and in severe cases, can cause the shaft 2 and the bearing 3 to cut into each other.

[0056] Based on this, the present disclosure provides a compressor that can alleviate the problem of impurities mixing between the rotating shaft 2 and the bearing 3.

[0057] In some embodiments, as Figure 1 As shown, the compressor includes a housing 1 , a rotating shaft 2 , a bearing 3 and a seal 4 .

[0058] The rotating shaft 2 is rotatably disposed in the housing 1 .

[0059] The bearing 3 is fixedly disposed in the housing 1 and is provided with a first hole for allowing the rotating shaft 2 to pass through. Optionally, the bearing 3 comprises a hydrodynamic gas bearing.

[0060] The seal 4 is fixed to the end of the bearing 3. The seal 4 is provided with a second hole allowing the shaft 2 to pass through. The hole wall of the second hole is provided with at least one first groove 41 (such as Figure 2 As shown), the first groove 41 is used to receive the liquid refrigerant and solid impurities in the fluid flowing into the first gap.

[0061] In a compressor, bearing 3 is located between pneumatic cavity 8 and first motor cavity 91. When liquid is carried by air or motor cooling is insufficient, liquid refrigerant will enter the gap between bearing 3 and shaft 2 along with the gaseous refrigerant. A small amount of liquid refrigerant is beneficial for bearing lubrication and cooling, but excessive liquid refrigerant will occupy the first gap between bearing 3 and shaft 2, disrupting the original air film balance and causing shaft system instability.

[0062] Therefore, in some embodiments, a first groove 41 is provided on the wall of the second hole. When the mixed refrigerant mixed with small particle impurities and a small amount of residual liquid refrigerant passes through the first groove 41, the small particle impurities and liquid refrigerant with relatively large gravity are separated under the action of gravity and enter the first groove 41, which can effectively prevent solid impurities and liquid refrigerant from entering the first gap.

[0063] In some embodiments, a first gap is formed between the first hole and the rotating shaft 2 , and a second gap is formed between the second hole and the rotating shaft 2 , and the second gap is smaller than or equal to the first gap.

[0064] To prevent large impurities from entering the first gap along with the gaseous refrigerant, a small gap is formed between the inner diameter surface of the seal 4 (the wall of the second hole) and the corresponding outer surface of the shaft 2. To achieve the best sealing effect, the second gap is smaller than the first gap.

[0065] To ensure the reliability of the rotating shaft 2 , the material hardness of the sealing member 4 is lower than that of the rotating shaft 2 . Optionally, the sealing member 4 is made of aluminum alloy.

[0066] Optionally, the second gap is 2 to 4 wires smaller than the first gap.

[0067] In some embodiments, the second gap between the seal 4 and the rotating shaft 2 is set to be very small. When the rotating shaft 2 rotates, the rotating shaft 2 and the seal 4 rub against each other. Through friction loss, the second gap between the seal 4 and the rotating shaft 2 adapts to reach an appropriate gap size.

[0068] Since the seal 4 is provided at the end of the bearing 3 and is located upstream of the fluid, the fluid here is the fluid flowing toward the first gap between the rotating shaft 2 and the bearing 3, and since the second gap formed between the seal 4 and the rotating shaft 2 is smaller than or equal to the first gap, impurities mixed in the fluid will be blocked by the seal 4 and prevented from mixing into the first gap.

[0069] In some embodiments, the second gap between the seal 4 and the rotating shaft 2 is smaller than the first gap to filter large particles of impurities; combined with the first groove 41, the flow area of ​​the refrigerant suddenly changes, causing the flow rate to stagnate, making it difficult for small particles of impurities to flow into the first gap.

[0070] In some embodiments, at least one first groove 41 includes a plurality of first annular grooves arranged around the axis of the rotating shaft 2 , and annular teeth are formed between two adjacent first annular grooves to form a comb-teeth seal between the hole wall of the second hole and the rotating shaft 2 .

[0071] In other embodiments, at least one first groove 41 includes a spiral groove arranged around the axis of the rotating shaft 2, and teeth are formed between two adjacent grooves in the spiral groove to form a comb-teeth seal between the hole wall of the second hole and the rotating shaft 2.

[0072] To prevent small particles and a small amount of residual liquid refrigerant from entering the first gap along with the gaseous refrigerant, a plurality of first grooves 41 are formed on the inner diameter surface of the seal 4 (the wall of the second hole). The operating principle is as follows: When the mixed refrigerant containing small particles and a small amount of residual liquid refrigerant passes through the small gap between each tooth and the rotating shaft 2, it undergoes an approximately ideal throttling process, with its pressure and temperature decreasing and its speed increasing. Upon entering the first groove 41, the flow area suddenly increases, causing the mixed refrigerant to form a strong vortex, with the pressure remaining unchanged but the speed almost completely disappearing. At this point, the small particles with relatively greater gravity and the liquid refrigerant are separated under the action of gravity. Through the multi-tooth groove structure, the above process is continuously repeated, effectively separating the small particles and a small amount of residual liquid refrigerant carried by the gaseous refrigerant.

[0073] In some embodiments, the second gap between the seal 4 and the rotating shaft 2 is smaller than the first gap to filter out large particles of impurities; combined with the principle of rotary pressure reduction of the comb seal, through the screening of multiple teeth and grooves, small particles of impurities are difficult to flow into the first gap, solving the problem of impurities mixing between the bearing 3 and the rotating shaft 2.

[0074] In some embodiments, the axial dimension of the top of the first groove 41 is greater than the axial dimension of the bottom of the first groove 41, and the top of the first groove 41 is closer to the rotating shaft 2 than the bottom of the first groove 41. Due to the principle of flow velocity stagnation caused by the sudden change in the flow area of ​​the first groove 41, small impurities are difficult to flow into the first gap.

[0075] In some embodiments, as Figure 2 As shown, the first groove 41 includes a first side wall 411 and a second side wall, the first side wall 411 is close to the bearing 3 relative to the second side wall, and the first side wall 411 extends radially along the rotating shaft 2, and the section of the second side wall located at the top of the first groove 41 is away from the bearing 3 relative to the section located at the bottom of the first groove 41.

[0076] The opening of the first groove 41 points to the side away from the bearing 3. On the one hand, it allows the "thrown" liquid refrigerant to stay away from the bearing 3; on the other hand, the "thrown" liquid refrigerant is in the opposite direction of the flow of the mixed refrigerant entering the bearing 3, so that the "thrown" liquid refrigerant has a certain blocking effect on the incoming mixed refrigerant.

[0077] In some embodiments, the contact and connection portion between the seal 4 and the bearing 3 is the side wall of the first groove 41 , and the bearing 3 is axially positioned via the side wall of the first groove.

[0078] In some embodiments, as Figure 1 As shown, seals 4 are provided at both ends of the bearing 3 along the axial direction of the rotating shaft 2 .

[0079] Because bearing 3 comprises a bearing body, elastic foil 31, and top foil 32, to achieve sufficient damping, the elastic foil is typically axially non-fixed, allowing for relative displacement with the bearing body and top foil, generating damping through Coulomb friction. Therefore, if the relative displacement is excessive or if significant axial misalignment occurs during assembly of bearing 3 and shaft 2, there is a risk that elastic foil 31 may axially escape from the bearing, causing bearing failure.

[0080] Therefore, in some embodiments, seals 4 are provided at both ends of the bearing 3 along the axial direction of the rotating shaft 2, and the contact and connection portion between the seal 4 and the bearing 3 is the side wall of the first groove 41. By positioning the seals 4 at both ends of the bearing 3, the problem of lack of axial positioning of the elastic foil 31 and large axial displacement of the elastic foil 31 causing bearing failure is solved.

[0081] In some embodiments, the seal 4 integrates the functions of comb-teeth sealing and axial positioning, has a compact structure, prevents impurities from entering the first gap, and prevents large axial displacement of the elastic foil from causing bearing failure.

[0082] In some embodiments, as Figure 2 As shown, since seal 4 is provided with a second through hole, seal 4 is an annular member, comprising a first annular portion 42 and a second annular portion 43. The outer diameter of first annular portion 42 is larger than the outer diameter of second annular portion 43. First annular portion 42 is fixedly connected to bearing 3, and second annular portion 43 is connected to first annular portion 42. Second annular portion 43 extends axially of shaft 2 away from bearing 3. The cooperation between second annular portion 43 and second annular portion 43 increases the mating area between seal 4 and shaft 2.

[0083] In some embodiments, at least one second groove 21 is provided on the rotating shaft 2 near the seal 4 , and the second groove 21 is away from the bearing 3 relative to the seal 4 .

[0084] To prevent liquid refrigerant from entering the gap between bearing 3 and shaft 2, a second groove 21 is provided on shaft 2, serving as a primary liquid-blocking seal. During operation, the second groove 21 uses the centrifugal force of high-speed rotation to "spin" out most of the liquid refrigerant, separating the mixed refrigerant from the gas and liquid, and preventing the liquid refrigerant from entering the primary gap.

[0085] In some embodiments, a second groove 21 is provided on the rotating shaft 2 near the seal 4 , combined with the comb-teeth sealing structure of the seal 4 , to alleviate the problem of excessive liquid refrigerant entering between the rotating shaft 2 and the bearing 3 and destroying the bearing pressure film.

[0086] Since there is liquid refrigerant in the first motor cavity 91, the pneumatic cavity 8 inhales air with liquid and also accumulates liquid refrigerant. Therefore, in some embodiments, a seal 4 is provided at both ends of the bearing 3 along the axial direction of the rotating shaft 2, and at least one second groove 21 is provided at a portion of the rotating shaft 2 close to the seal 4, and the second groove 21 is away from the bearing 3 relative to the seal 4.

[0087] To prevent liquid refrigerant from entering the first gap, second grooves 21 are provided on the rotating shaft 2, at both ends of the bearing 3. These second grooves 21 serve as a primary liquid-blocking seal. During operation, the centrifugal force of the high-speed rotation of the second grooves 21 ejects most of the liquid refrigerant, separating the gas and liquid in the mixed refrigerant. The remaining small amount of liquid refrigerant is blocked by the comb-shaped seal structure of the seal 4, preventing it from entering the first gap.

[0088] In some embodiments, an outlet may also be provided on the side wall of the shell 1 corresponding to the pneumatic cavity 8 to lead out the liquid refrigerant in the pneumatic cavity 8 .

[0089] In some embodiments, the axial dimension of the top of the second groove 21 is greater than the axial dimension of the bottom of the second groove 21. The bottom of the second groove 21 is closer to the central axis of the rotating shaft 2 than the top of the second groove 21.

[0090] In some embodiments, the second groove 21 includes a third side wall and a fourth side wall, the third side wall is close to the bearing 3 relative to the fourth side wall, and the third side wall extends radially along the rotating shaft 2, and the section of the fourth side wall located at the top of the second groove 21 is away from the bearing 3 relative to the section located at the bottom of the second groove 21.

[0091] To achieve efficient gas-liquid separation, the opening of the second groove 21 points away from the bearing 3. On the one hand, this keeps the "expelled" liquid refrigerant away from the bearing 3; on the other hand, the "expelled" liquid refrigerant flows in the opposite direction to the mixed refrigerant entering the first gap, so that the "expelled" liquid refrigerant has a certain blocking effect on the incoming mixed refrigerant.

[0092] In some embodiments, the at least one second groove 21 includes a plurality of second annular grooves arranged around the axis of the rotating shaft 2 .

[0093] In some embodiments, the at least one second groove 21 comprises a spiral groove disposed around the axis of the rotating shaft 2 .

[0094] Some embodiments provide an air conditioner comprising the above-mentioned compressor.

[0095] The air conditioner includes a refrigeration cycle system, and the refrigerant in the compressor comes from the refrigerant in the refrigeration cycle system.

[0096] The air conditioner includes a refrigeration cycle system formed by a condenser, an evaporator and a compressor.

[0097] In the description of the present invention, it should be understood that the use of terms such as "first", "second", and "third" to limit components is only for the convenience of distinguishing the above components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present invention.

[0098] In addition, unless explicitly denied, the technical features of one embodiment may be beneficially combined with one or more other embodiments.

[0099] Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the present invention and not to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, ordinary technicians in the field should understand that the specific implementation methods of the present invention can still be modified or some technical features can be replaced by equivalents without departing from the spirit of the technical solution of the present invention. They should all be included in the scope of the technical solution for protection of the present invention.

Claims

1. A compressor, characterized in that: include: housing (1); A rotating shaft (2) is rotatably disposed in the housing (1); A bearing (3) is fixedly arranged in the housing (1), the bearing (3) being provided with a first hole allowing the rotating shaft (2) to pass through; a first gap is formed between the hole wall of the first hole and the rotating shaft (2); the bearing (3) comprises a dynamic pressure gas bearing; and a sealing member (4) fixedly disposed at an end portion of the bearing (3), the sealing member (4) being provided with a second hole allowing the rotating shaft (2) to pass therethrough, a second gap being formed between a hole wall of the second hole and the rotating shaft (2), and at least one first groove (41) being provided on the hole wall of the second hole; The sealing members (4) are provided at both ends of the bearing (3) along the axial direction of the rotating shaft (2); At least one second groove (21) is provided on the rotating shaft (2) at a position close to the sealing member (4), and the second groove (21) is away from the bearing (3) relative to the sealing member (4); The openings of the first groove (41) and the second groove (21) are directed toward a side away from the bearing (3).

2. The compressor according to claim 1, wherein The second gap is smaller than or equal to the first gap.

3. The compressor according to claim 1, wherein The at least one first groove (41) comprises a plurality of first annular grooves arranged around the axis of the rotating shaft (2), and annular teeth are formed between two adjacent first annular grooves, so that a comb-teeth seal is formed between the hole wall of the second hole and the rotating shaft (2).

4. The compressor according to claim 1, wherein The at least one first groove (41) comprises a spiral groove arranged around the axis of the rotating shaft (2).

5. The compressor according to claim 1, wherein The axial dimension of the groove top of the first groove (41) is greater than the axial dimension of the groove bottom, and the groove top of the first groove (41) is closer to the rotating shaft (2) relative to the groove bottom.

6. The compressor according to claim 5, characterized in that The first groove (41) comprises a first side wall (411) and a second side wall, wherein the first side wall (411) is closer to the bearing (3) relative to the second side wall, and the first side wall (411) extends radially along the rotating shaft (2), and a section of the second side wall located at the top of the groove is farther away from the bearing (3) relative to a section located at the bottom of the groove.

7. The compressor according to claim 1, wherein The contact connection portion between the sealing member (4) and the bearing (3) is the side wall of the first groove (41).

8. The compressor according to claim 1, wherein The sealing member (4) comprises a first annular portion (42) and a second annular portion (43), wherein the outer diameter of the first annular portion (42) is larger than the outer diameter of the second annular portion (43), the first annular portion (42) is fixedly connected to the bearing (3), the second annular portion (43) is connected to the first annular portion (42), and the second annular portion (43) extends in an axial direction of the rotating shaft (2) in a direction away from the bearing (3).

9. The compressor according to claim 1, wherein The axial dimension of the groove top of the second groove (21) is greater than the axial dimension of the groove bottom, wherein the groove bottom of the second groove (21) is closer to the central axis of the rotating shaft (2) relative to the groove top.

10. The compressor according to claim 9, wherein The second groove (21) comprises a third side wall and a fourth side wall, the third side wall being closer to the bearing (3) relative to the fourth side wall, and the third side wall extending radially along the rotating shaft (2), and the section of the fourth side wall located at the top of the groove being farther away from the bearing (3) relative to the section located at the bottom of the groove.

11. The compressor according to claim 1, wherein The at least one second groove (21) comprises a plurality of second annular grooves arranged around the axis of the rotating shaft (2) or a spiral groove arranged around the axis of the rotating shaft (2).

12. An air conditioner, characterized in that: The invention comprises a compressor according to any one of claims 1 to 11.

Images