CN113107895A - Compressor and air conditioner - Google Patents

Abstract

The invention relates to a compressor and an air conditioner. Wherein, the compressor includes: a housing; the rotating shaft is rotatably arranged in the shell; the bearing is fixedly arranged in the shell and provided with a first hole allowing the rotating shaft to pass through; and the sealing element is fixedly arranged at the end part of the bearing, the sealing element is provided with a second hole allowing the rotating shaft to pass through, and the hole wall of the second hole is provided with at least one first groove. When the mixed refrigerant mixed with the small particle impurities and the residual few liquid refrigerants passes through the first groove, the small particle impurities with relatively large gravity and the liquid refrigerants are separated under the action of gravity and enter the first groove, and the solid impurities and the liquid refrigerants can be effectively prevented from entering the space between the rotating shaft and the bearing.

Description

Compressor and air conditioner

Technical Field

The invention relates to the field of compressors, in particular to a compressor and an air conditioner.

Background

The bearing is a transmission part which is not necessary to be lacked in the modern mechanical equipment and mainly plays a supporting role. The massage eraser has different properties, and the bearings can be divided into rolling bearings, sliding bearings, magnetic suspension bearings and air suspension bearings. The air bearing has the advantages of small friction loss, almost no friction at extremely high rotating speed, good high-temperature stability, small vibration, no need of lubricating oil and the like, is applied to the high-speed turbine field of a centrifugal compressor and the like, and has very wide application prospect.

The air bearings are classified into static pressure gas bearings and dynamic pressure gas bearings according to the difference in the mechanism of generation of a lubricating gas film. The static pressure gas bearing utilizes an external gas source to supply gas to the bearing to generate pressure bearing load. The dynamic pressure gas bearing supports a load by a pressure gas film generated by gas in a wedge-shaped space between a shaft and an inner surface of the bearing. When the shaft rotates at a high speed, gas with certain viscosity is continuously brought into the wedge-shaped gap, the gas continuously enters the wedge-shaped gap to enable the gas film to generate certain pressure, when the force of the gas film is enough to balance external load, the bearing and the surface of the shaft generate a complete pressure lubrication gas film, the shaft is completely separated from the bearing, and the friction force basically disappears; the damping of the dynamic pressure bearing is generated by the mutual dislocation friction among the bearing shell, the top foil and the elastic foil.

In summary, a pressure gas film is formed between the shaft and the bearing through gas entering, however, the related dynamic pressure bearing has the problem that impurities and excessive liquid are mixed between the shaft and the bearing during operation, and the pressure gas film is damaged.

Disclosure of Invention

One of the objects of the present invention is to provide a compressor and an air conditioner for alleviating the problem of impurities mixed between a shaft and a bearing.

Some embodiments of the present invention provide a compressor, including:

a housing;

the rotating shaft is rotatably arranged in the shell;

the bearing is fixedly arranged in the shell and provided with a first hole allowing the rotating shaft to pass through; and

the sealing element is fixedly arranged at the end part of the bearing and provided with a second hole allowing the rotating shaft to pass through, and the hole wall of the second hole is provided with at least one first groove.

In some embodiments, a first gap is formed between the wall of the first hole and the shaft, and a second gap is formed between the wall of the second hole and the shaft, the second gap being less than or equal to the first gap.

In some embodiments, the at least one first groove comprises 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, so that a comb tooth seal is formed between the hole wall of the second hole and the rotating shaft.

In some embodiments, the at least one first groove comprises a helical groove disposed about the axis of the shaft.

In some embodiments, the axial dimension of the slot top of the first slot is greater than the axial dimension of the slot bottom, the slot top of the first slot being closer to the shaft than the slot bottom.

In some embodiments, the first groove includes a first sidewall and a second sidewall, the first sidewall is close to the bearing relative to the second sidewall, and the first sidewall extends in a radial direction of the rotating shaft, and a section of the second sidewall at a top of the groove is away from the bearing relative to a section at a bottom of the groove.

In some embodiments, the portion of the seal in contact with the bearing is a sidewall of the first groove.

In some embodiments, the bearing is provided with the sealing member at both ends in the axial direction of the rotating shaft.

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 in a direction away from the bearing along the axial direction of the rotating shaft.

In some embodiments, the shaft is provided with at least one second groove at a position close to the seal, and the second groove is far away from the bearing relative to the seal.

In some embodiments, the bearing is provided with a sealing element at both ends in the axial direction of the rotating shaft, and the rotating shaft is provided with at least one second groove at a position close to the sealing element, and the second groove is far away from the bearing relative to the sealing element.

In some embodiments, the second groove has a groove top with an axial dimension greater than an axial dimension of a groove bottom, wherein the groove bottom of the second groove is proximate to the central axis of the shaft relative to the groove top.

In some embodiments, the second groove includes a third sidewall and a fourth sidewall, the third sidewall being proximate to the bearing relative to the fourth sidewall and extending in a radial direction of the shaft, a section of the fourth sidewall at a top of the groove being distal from the bearing relative to a section at a bottom of the groove.

In some embodiments, the at least one second groove comprises a plurality of second annular grooves disposed about the axis of the rotating shaft or a helical groove disposed about the axis of the rotating shaft.

Some embodiments of the present invention provide an air conditioner including the compressor described above.

Based on the technical scheme, the invention at least has the following beneficial effects:

in some embodiments, the sealing member is fixedly disposed at an end portion of the bearing, the sealing member is provided with a second hole allowing the rotating shaft to pass through, a hole wall of the second hole is provided with at least one first groove, when a mixed refrigerant mixed with small particle impurities and a residual small amount of liquid refrigerant passes through the first groove, the small particle impurities and the liquid refrigerant with relatively large gravity are separated under the action of gravity and enter the first groove, and the solid impurities and the liquid refrigerant can be effectively prevented from entering between the rotating shaft and the bearing.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:

FIG. 1 is a schematic illustration in partial cross-section of a compressor provided in accordance with some embodiments of the present invention;

fig. 2 is an enlarged schematic view of a portion a in fig. 1.

Reference numerals in the drawings indicate:

1-a shell; 11-a spiral flow channel; 12-a refrigerant inlet; 13-refrigerant outlet;

2-a rotating shaft; 21-a second groove;

3-a bearing; 31-an elastic foil; 32-top foil;

4-a seal; 41-a first groove; 411 — first side wall; 42-a first annular portion; 43-a second annular portion;

5-bearing support;

6-a motor stator; 61-a first channel;

7-a second channel;

8-a pneumatic chamber;

91-a first motor cavity; 92-second motor cavity.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments. It is to be understood that the described embodiments are merely a few embodiments of the invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments of the present invention without any inventive step, are within the scope of the present invention.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are used merely for convenience in describing the present invention and for simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be taken as limiting the scope of the present invention.

As shown in fig. 1, the compressor includes a housing 1, a rotating shaft 2, a bearing 3, a bearing support 5, and a motor stator 6.

The cavity formed by the shell 1 is irregular, and the shell 1 is generally formed by casting and has the functions of supporting, protecting, absorbing shock and the like.

The rotating shaft 2 is a shaft and a solid part and is an important component of the motor. The rotating shaft 2 is rotatably arranged in the shell 1. When the electromagnetic field-driven rotating shaft works, the rotating shaft 2 rotates at a high speed under the action of the electromagnetic field. The rotating shaft 2 is a motor rotor in the compressor.

The motor stator 6 is a rotary part, is an important component of the motor and mainly comprises a winding, and the motor stator 6 is arranged in the shell 1 and fixed on the shell 1. The motor stator 6 is provided with a first channel 61 inside, and the first channel 61 is close to the outer edge of the motor stator 6. The rotating shaft 2 penetrates through the motor stator 6, and a gap is formed between the rotating shaft 2 and the motor stator 6 to form a second channel 7.

The rotating shaft 2 penetrates through the motor stator 6, a bearing 3 is arranged at the position, close to the first end of the motor stator 6, of the rotating shaft 2, and another bearing 3 is arranged at the position, close to the second end of the motor stator 6, of the rotating shaft 2.

The bearing support 5 is disposed in the housing 1 and connected to the housing 1. The bearing support 5 is provided with a through hole, and the bearing 3 is fixedly arranged in the through hole of the bearing support 5. The bearing 3 is provided with a through hole for the rotating shaft 2 to pass through. The bearing 3 comprises a bearing body, a flexible foil 31 and a top foil 32. The top foil 32 is close to the rotation shaft 2 with respect to the elastic foil 31.

In order to realize that the bearing 3 provided with the elastic foil 31 and the top foil 32 has good coaxiality with the rotating shaft 2, the shell 1, the bearing support 5 and the bearing 3 are pre-assembled together and then provided with a through hole which is arranged on the bearing 3 and allows the rotating shaft 2 to pass through; or, the housing 1 and the bearing support 5 are pre-assembled together, and then the bearing support 5 is provided with a through hole allowing the rotating shaft 2 to pass through and being capable of being provided with the bearing 3.

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

The inner wall of the shell 1 is provided with a spiral groove, and the spiral groove is matched with the motor stator 6 to form a spiral flow passage 11. The side wall of the housing 1 is further provided with a refrigerant inlet 12 and a refrigerant outlet 13. The refrigerant inlet 12 is close to the second motor cavity 92, and the refrigerant outlet 13 is disposed on the side wall of the housing 1 corresponding to the second motor cavity 92.

When the motor works, a refrigerant is introduced into the refrigerant inlet 12, enters the spiral flow passage 11 and flows in the spiral flow passage 11 to cool the motor, the refrigerant after cooling the motor enters the first motor cavity 91 from the spiral flow passage 11, and at the moment, part of the refrigerant is gasified and is still liquid. Under the condition that the bearing 3 is a pneumatic bearing, the heat-absorbing gasified refrigerant part enters the bearing 3, the rest of the refrigerant flows to the second motor cavity 92 from the second channel 7, the refrigerant outlet 13 is communicated with the second motor cavity 92, and the refrigerant outlet 13 is also connected with the evaporator, so that the pressure of the second motor cavity 92 is lower than that of the first motor cavity 91, and the gaseous refrigerant flows to the second motor cavity 92 from the first motor cavity 91 through the pressure difference effect.

The liquid refrigerant that still is not gasified after the heat transfer remains in first motor chamber 91, for avoiding first motor chamber 91 bottom hydrops, causes to take liquid hidden danger to bearing 3, motor stator 6 is inside to be set up first passageway 61, first passageway 61 intercommunication motor stator 6 first motor chamber 91 and second motor chamber 92 at both ends. During operation, when the liquid level of the first motor cavity 91 reaches the pressure difference of the first channel 61, the liquid refrigerant in the first motor cavity 91 flows to the second motor cavity 92 through the first channel 61 quickly, and flows out through the refrigerant outlet 13.

The cavity of the bearing support 5 and the end of the bearing 3 far away from the motor stator 6 is a pneumatic cavity 8, the pneumatic cavity 8 is formed by the shell 1 and pneumatic parts (such as an impeller, a diffuser and the like), and the pneumatic cavity 8 is communicated with the dynamic pressure bearing and the pneumatic parts and is one of source channels of air sources required by the dynamic pressure bearing. The first motor chamber 91 is another source of air supply for the hydrodynamic bearing.

The dynamic pressure bearing supports a load by a pressure film generated by gas in a wedge-shaped space between a shaft and an inner surface of the bearing. When the rotating shaft 2 rotates at a high speed, gas with certain viscosity is continuously brought between the rotating shaft 2 and the bearing 3, the gas continuously enters to enable the gas film to generate certain pressure, when the force of the gas film is enough to balance external load, the bearing 3 and the surface of the rotating shaft 2 generate a complete pressure lubrication gas film, the rotating shaft 2 is completely separated from the bearing 3, and the friction force basically disappears.

The gas enters between the rotating shaft 2 and the bearing 3 to form a pressure gas film, and gas impurities are mixed between the rotating shaft 2 and the bearing 3 due to the lack of a filtering device. Because the bearing 3 comprises the elastic foil structure, a small amount of impurities can be tolerated due to the particularity of the elastic foil structure, but when the impurities are excessive, the impurities can cause scratches slightly, and when the impurities are excessive, the rotating shaft 2 and the bearing 3 can be cut into threads mutually.

Based on this, the present disclosure provides a compressor capable of alleviating the problem of impurities being mixed between the rotating shaft 2 and the bearing 3.

In some embodiments, as shown in fig. 1, the compressor includes a housing 1, a shaft 2, a bearing 3, and a seal 4.

The rotating shaft 2 is rotatably arranged in the shell 1.

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

The sealing element 4 is fixedly arranged at the end part of the bearing 3, the sealing element 4 is provided with a second hole allowing the rotating shaft 2 to pass through, the hole wall of the second hole is provided with at least one first groove 41 (shown in fig. 2), and the first groove 41 is used for receiving liquid refrigerant and solid impurities in the fluid flowing to the first gap.

In the compressor, the bearing 3 is positioned between the pneumatic cavity 8 and the first motor cavity 91, and when the conditions of air suction with liquid or insufficient cooling of the motor and the like occur, liquid refrigerant enters between the bearing 3 and the rotating shaft 2 along with gaseous refrigerant. A small amount of liquid refrigerant is beneficial to bearing lubrication and cooling, but the liquid refrigerant enters too much to occupy a first gap between the bearing 3 and the rotating shaft 2, and the original air film balance is damaged, so that shafting instability is caused.

Therefore, in some embodiments, the first groove 41 is formed on the wall of the second hole, and when the mixed refrigerant mixed with the small particle impurities and the remaining small amount of liquid refrigerant passes through the first groove 41, the small particle impurities and the liquid refrigerant with relatively large gravity are separated under the action of gravity and enter the first groove 41, so that the solid impurities and the liquid refrigerant can be effectively prevented from entering the first gap.

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, wherein the second gap is smaller than or equal to the first gap.

In order to prevent large particle impurities from entering the first gap along with the gaseous refrigerant, a small clearance fit is formed between the inner diameter surface (the hole wall of the second hole) of the sealing element 4 and the corresponding outer surface of the rotating shaft 2. For optimal sealing, the second gap is smaller than the first gap.

In order to ensure the reliability of the rotating shaft 2, the material hardness of the sealing element 4 is lower than that of the rotating shaft 2, and optionally, the sealing element 4 is made of aluminum alloy.

Optionally, the second gap is 2-4 filaments smaller than the first gap.

In some embodiments, the second gap between the sealing element 4 and the rotating shaft 2 is set to be small, and when the rotating shaft 2 rotates, the rotating shaft 2 and the sealing element 4 rub, and the second gap between the sealing element 4 and the rotating shaft 2 is self-adapted to reach an appropriate gap size through friction loss.

Because the sealing member 4 is disposed at the end of the bearing 3 and located at the upstream of the fluid, the fluid therein is the fluid flowing to the first gap between the rotating shaft 2 and the bearing 3, and the second gap formed between the sealing member 4 and the rotating shaft 2 is smaller than or equal to the first gap, the impurities mixed in the fluid can be blocked by the sealing member 4, and are prevented from being mixed in the first gap.

In some embodiments, the second gap between the seal 4 and the shaft 2 is smaller than the first gap to filter large particle impurities; and the first groove 41 is combined, so that the flow velocity is stopped due to the sudden change of the flow area of the refrigerant, and small particle impurities are difficult to flow into the first gap.

In some embodiments, the at least one first groove 41 includes a plurality of first annular grooves disposed around the axis of the rotating shaft 2, and annular teeth are formed between two adjacent first annular grooves, so that a comb seal is formed between the wall of the second hole and the rotating shaft 2.

In other embodiments, the at least one first groove 41 comprises a helical groove disposed about the axis of the shaft 2, and adjacent ones of the helical grooves form teeth therebetween, such that a comb seal is formed between the wall of the second bore and the shaft 2.

In order to prevent small particle impurities and a small amount of remaining 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 (the hole wall of the second hole) of the sealing member 4. The working principle is as follows: when the mixed refrigerant mixed with small particle impurities and residual few liquid refrigerants passes through the small gap between each tooth and the rotating shaft 2, the throttling process is approximate to an ideal throttling process, the pressure and the temperature of the mixed refrigerant are reduced, and the speed is increased; when the refrigerant enters the first groove 41, the mixed refrigerant forms a strong vortex due to the suddenly increased flow area, the pressure is unchanged but the speed almost completely disappears, and at the moment, small particle impurities with relatively large gravity and the liquid refrigerant are separated under the action of gravity; through multichannel tooth's socket structure, constantly repeat above-mentioned process, the small granule impurity that carries and remaining few liquid refrigerant in the effective separation gaseous state refrigerant.

In some embodiments, the second gap between the seal 4 and the shaft 2 is smaller than the first gap to filter large particle impurities; the principle of the sealed rotatory step-down of broach combines, through the screening of multiple tooth's socket for the tiny particle impurity is difficult to flow into first clearance, solves the problem of sneaking into impurity between bearing 3 and the pivot 2.

In some embodiments, the axial dimension of the groove top of the first groove 41 is greater than the axial dimension of the groove bottom of the first groove 41, the groove top of the first groove 41 being closer to the rotation shaft 2 than the groove bottom of the first groove 41. The small particle impurities are hard to flow into the first gap by the principle of the flow velocity stagnation caused by the abrupt change of the flow area of the first groove 41.

In some embodiments, as shown in fig. 2, 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 in a radial direction of the rotation shaft 2, and a section of the second side wall located at a groove top of the first groove 41 is away from the bearing 3 relative to a section located at a groove bottom of the first groove 41.

The opening of the first groove 41 points to the side far away from the bearing 3, on one hand, so that the liquid refrigerant which is thrown out is far away from the bearing 3; on the other hand, the direction of the incoming flow of the liquid refrigerant which is "thrown off" is opposite to the direction of the incoming flow of the mixed refrigerant entering the bearing 3, so that the liquid refrigerant which is "thrown off" plays a certain role in blocking the incoming flow of the mixed refrigerant.

In some embodiments, the contact portion of the sealing member 4 and the bearing 3 is a sidewall of the first groove 41, and the bearing 3 is axially positioned by the sidewall of the first groove.

In some embodiments, as shown in fig. 1, the bearing 3 is provided with a sealing member 4 at both ends in the axial direction of the rotating shaft 2.

Since the bearing 3 comprises the bearing body, the elastic foil 31 and the top foil 32, in order to obtain sufficient damping, the elastic foil is generally axially non-fixed so as to be displaced relative to the bearing body and the top foil, and the damping is generated by coulomb friction. When the relative displacement is too large or the axial pulling misalignment occurs when the bearing 3 is assembled with the rotating shaft 2, there is a possibility that the elastic foil 31 may come out of the bearing from the axial direction, resulting in the failure of the bearing.

Therefore, in some embodiments, the two ends of the bearing 3 in the axial direction of the rotating shaft 2 are provided with the sealing elements 4, and the contact connection part of the sealing elements 4 and the bearing 3 is the side wall of the first groove 41, so that the problem that the elastic foil 31 lacks axial positioning and the elastic foil 31 axially displaces and moves to cause bearing failure is solved through the positioning of the sealing elements 4 at the two ends of the bearing 3.

In some embodiments, the sealing element 4 integrates the functions of comb sealing and axial positioning, has a compact structure, avoids the first gap from being mixed with impurities, and avoids the elastic foil from causing bearing failure due to large axial displacement and play.

In some embodiments, as shown in fig. 2, since the sealing member 4 is provided with the second through hole, the sealing member 4 is an annular member, the annular member includes a first annular portion 42 and a second annular portion 43, an outer diameter of the first annular portion 42 is larger than an outer diameter of the second annular portion 43, the first annular portion 42 is fixedly connected with the bearing 3, the second annular portion 43 is connected with the first annular portion 42, and the second annular portion 43 extends in a direction away from the bearing 3 along the axial direction of the rotating shaft 2. The second annular portion 43 cooperates with the second annular portion 43 to increase the area of cooperation of the seal 4 with the rotary shaft 2.

In some embodiments, the shaft 2 is provided with at least one second groove 21 at a location adjacent to the seal 4, the second groove 21 being distal from the bearing 3 relative to the seal 4.

In order to prevent the liquid refrigerant from entering between the bearing 3 and the rotating shaft 2, a second groove 21 is formed on the rotating shaft 2 to serve as a first liquid-blocking seal. When the air conditioner works, the second groove 21 utilizes centrifugal force of high-speed rotation to throw out most of liquid refrigerants, gas-liquid separation is carried out on mixed refrigerants, and the liquid refrigerants are prevented from entering the first gap.

In some embodiments, the second groove 21 is disposed on the rotating shaft 2 near the sealing element 4, and the comb sealing structure of the sealing element 4 is used to alleviate the problem that the excessive liquid refrigerant enters between the rotating shaft 2 and the bearing 3 to break the pressure film of the bearing.

Because the first motor cavity 91 has liquid refrigerant, the pneumatic cavity 8 sucks air and carries liquid, and also accumulates liquid refrigerant, in some embodiments, the two ends of the bearing 3 along the axial direction of the rotating shaft 2 are both provided with a sealing member 4, the part of the rotating shaft 2 close to the sealing member 4 is both provided with at least one second groove 21, and the second groove 21 is far away from the bearing 3 relative to the sealing member 4.

In order to prevent the liquid refrigerant from entering the first gap, the second grooves 21 are formed in the rotating shaft 2 and located at two ends of the bearing 3, and the second grooves 21 are used as first liquid-blocking seals. During operation, the second groove 21 utilizes centrifugal force of high-speed rotation to throw out most of liquid refrigerants, gas-liquid separation is carried out on mixed refrigerants, and the rest of liquid refrigerants are blocked through the comb tooth sealing structure on the sealing element 4, so that the liquid refrigerants are prevented from entering the first gap.

In some embodiments, the sidewall of the housing 1 corresponding to the pneumatic cavity 8 may also be provided with an outlet to lead out the liquid refrigerant in the pneumatic cavity 8.

In some embodiments, the axial dimension of the groove top of the second groove 21 is greater than the axial dimension of the groove bottom of the second groove 21. Wherein the bottom of the second groove 21 is close to the central axis of the rotating shaft 2 relative to the top of the second groove 21.

In some embodiments, the second groove 21 comprises a third sidewall and a fourth sidewall, the third sidewall being close to the bearing 3 with respect to the fourth sidewall, and the third sidewall extending in the radial direction of the rotation shaft 2, a section of the fourth sidewall located at the groove top of the second groove 21 being distant from the bearing 3 with respect to a section located at the groove bottom of the second groove 21.

To achieve an efficient gas-liquid separation, the opening of the second groove 21 is directed to the side facing away from the bearing 3. On one hand, the liquid refrigerant which is thrown out is far away from the bearing 3; on the other hand, the direction of the incoming flow of the liquid refrigerant which is thrown out is opposite to the direction of the incoming flow of the mixed refrigerant entering the first gap, so that the liquid refrigerant which is thrown out plays a certain role in blocking the incoming flow of the mixed refrigerant.

In some embodiments, the at least one second groove 21 comprises a plurality of second annular grooves disposed about the axis of the shaft 2.

In some embodiments, the at least one second groove 21 comprises a helical groove disposed about the axis of the shaft 2.

Some embodiments provide an air conditioner including the compressor described above.

The air conditioner comprises a refrigeration cycle system, and a refrigerant in a compressor is derived from the refrigerant in the refrigeration cycle system.

The air conditioner includes a refrigeration cycle system formed of a condenser, an evaporator and a compressor.

In the description of the present invention, it should be understood that the terms "first", "second", "third", etc. are used to define the components, and are used only for the convenience of distinguishing the components, and if not otherwise stated, the terms have no special meaning, and thus, should not be construed as limiting the scope of the present invention.

Furthermore, the technical features of one embodiment may be combined with one or more other embodiments advantageously without explicit negatives.

Finally, it should be noted that the above examples are only used to illustrate the technical solutions of the present invention and not to limit the same; although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art will understand that: modifications to the specific embodiments of the invention or equivalent substitutions for parts of the technical features may be made; without departing from the spirit of the present invention, it is intended to cover all aspects of the invention as defined by the appended claims.

Claims (15)

1. A compressor, comprising:

a housing (1);

the rotating shaft (2) is rotatably arranged in the shell (1);

the bearing (3) is fixedly arranged in the shell (1), and the bearing (3) is provided with a first hole allowing the rotating shaft (2) to penetrate through; and

the sealing element (4) is fixedly arranged at the end part of the bearing (3), a second hole allowing the rotating shaft (2) to penetrate through is formed in the sealing element (4), and at least one first groove (41) is formed in the hole wall of the second hole.

2. The compressor of claim 1, wherein a first clearance is formed between a bore wall of the first bore and the rotary shaft (2), and a second clearance is formed between a bore wall of the second bore and the rotary shaft (2), the second clearance being smaller than or equal to the first clearance.

3. The compressor of 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 seal is formed between the wall of the second hole and the rotating shaft (2).

4. Compressor according to claim 1, characterized in that said at least one first groove (41) comprises a helical groove arranged around the axis of said rotating shaft (2).

5. Compressor according to claim 1, characterized in that the axial dimension of the groove top of the first groove (41) is greater than the axial dimension of the groove bottom, the groove top of the first groove (41) being closer to the shaft (2) with respect to the groove bottom.

6. Compressor according to claim 5, characterized in that said first slot (41) comprises a first side wall (411) and a second side wall, said first side wall (411) being close to said bearing (3) with respect to said second side wall, and said first side wall (411) extending in the radial direction of said shaft (2), the section of said second side wall at the top of the slot being remote from said bearing (3) with respect to the section at the bottom of the slot.

7. Compressor according to claim 1, characterized in that the contact connection of the seal (4) with the bearing (3) is the side wall of the first groove (41).

8. The compressor according to claim 1, wherein the bearing (3) is provided with the seal (4) at both ends in the axial direction of the rotating shaft (2).

9. The compressor as claimed in claim 1, characterized in that the seal (4) comprises a first annular portion (42) and a second annular portion (43), the outer diameter of the first annular portion (42) being larger than the outer diameter of the second annular portion (43), the first annular portion (42) being fixedly connected with the bearing (3), the second annular portion (43) being connected with the first annular portion (42), and the second annular portion (43) extending in the axial direction of the rotary shaft (2) in a direction away from the bearing (3).

10. Compressor according to claim 1, characterized in that the shaft (2) is provided with at least one second groove (21) in a region close to the seal (4), the second groove (21) being remote from the bearing (3) with respect to the seal (4).

11. Compressor according to claim 1, characterized in that the bearing (3) is provided with a sealing element (4) at both ends in the axial direction of the shaft (2), and that the shaft (2) is provided with at least one second groove (21) at a location close to the sealing element (4), the second groove (21) being remote from the bearing (3) with respect to the sealing element (4).

12. Compressor according to claim 10 or 11, characterized in that 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 located close to the middle axis of the shaft (2) with respect to the groove top.

13. Compressor according to claim 12, characterized in that the second groove (21) comprises a third side wall and a fourth side wall, the third side wall being close to the bearing (3) with respect to the fourth side wall and extending in the radial direction of the shaft (2), the section of the fourth side wall at the top of the groove being remote from the bearing (3) with respect to the section at the bottom of the groove.

14. Compressor according to claim 10 or 11, characterized in that said at least one second groove (21) comprises a plurality of second annular grooves arranged around the axis of said rotating shaft (2) or helical grooves arranged around the axis of said rotating shaft (2).

15. An air conditioner characterized by comprising the compressor according to any one of claims 1 to 14.

Images