CN113323908A - Air compressor machine, air conditioner and car - Google Patents

Abstract

The utility model relates to an air compressor equipment technical field, in particular to air compressor machine. The air compressor machine includes: a housing, inside which a motor cavity is arranged; the motor is arranged in the motor cavity and comprises a stator and a rotor, and the rotor penetrates through the stator; a radial bearing disposed on the rotor; and the air cooling structure comprises a cooling air inlet, a cooling air outlet and a bearing air cooling runner, the cooling air inlet and the cooling air outlet are both arranged on the shell, and the bearing air cooling runner is arranged on the radial bearing and is communicated with the cooling air inlet and the cooling air outlet. Based on this, the cooling effect of the radial bearing in the air compressor can be improved.

Description

Air compressor machine, air conditioner and car

Technical Field

The disclosure relates to the technical field of air compression equipment, in particular to an air compressor, an air conditioner and an automobile.

Background

The air compressor is a mechanical device which compresses atmospheric air to transmit the air into high-pressure air for use by air supply equipment. The rotating speed of the air compressor is generally high, a large amount of heat can be generated, the heat can affect the service life of an inner stator, a rotor, a bearing and the like of the air compressor, and the performance of the air compressor is further affected.

In the related art, the cooling effect of the radial bearing in the air compressor is to be improved.

Disclosure of Invention

One technical problem to be solved by the present disclosure is: the cooling effect of the radial bearing in the air compressor is improved.

In order to solve the technical problem, the present disclosure provides an air compressor, which includes:

a housing, inside which a motor cavity is arranged;

the motor is arranged in the motor cavity and comprises a stator and a rotor, and the rotor penetrates through the stator;

a radial bearing disposed on the rotor; and

the air cooling structure comprises a cooling air inlet, a cooling air outlet and a bearing air cooling runner, wherein the cooling air inlet and the cooling air outlet are both arranged on the shell, and the bearing air cooling runner is arranged on the radial bearing and is communicated with the cooling air inlet and the cooling air outlet.

In some embodiments, the air compressor includes at least two radial bearings, and the at least two radial bearings include first radial bearing and second radial bearing, and first radial bearing and second radial bearing are located the axial both sides of stator and arrange in proper order along the direction by cooling air inlet to cooling air outlet, and the bearing air cooling runner includes first bearing runner and second bearing runner, and the first bearing runner sets up on first radial bearing, and the second bearing runner sets up on the second radial bearing, and first bearing runner and second bearing runner all communicate with the motor chamber.

In some embodiments, the first bearing flowpath includes a first radial flowpath extending in a radial direction of the rotor and a first axial flowpath extending in an axial direction of the rotor, the first radial flowpath being in communication with the cooling air inlet and with the motor cavity through the first axial flowpath; and/or the second bearing runner comprises a second axial runner and a second radial runner, the second axial runner extends along the axial direction of the rotor, the second radial runner extends along the radial direction of the rotor, and the second axial runner is communicated with the motor cavity and communicated with the cooling air outlet through the second radial runner.

In some embodiments, the air compressor includes an axial bearing disposed in the housing and located on a side of the second radial bearing away from the first radial bearing, and the second bearing flow passage communicates with the cooling air outlet through a space in which the axial bearing is located, so that the cooling air flowing out of the second bearing flow passage flows through the axial bearing in a process of flowing to the cooling air outlet, and cools the axial bearing.

In some embodiments, the air compressor includes a bearing seat, the bearing seat supports the radial bearing, a communication flow passage is provided on the bearing seat, and the cooling air inlet and/or the cooling air outlet are communicated with the bearing air cooling flow passage through the communication flow passage.

In some embodiments, the bearing air cooling flow passage is disposed on a bearing shell of the radial bearing.

In some embodiments, the air cooling structure includes a buffer chamber located within the housing and communicating the cooling air inlet and the bearing air cooling channel.

In some embodiments, the buffer chamber communicates the cooling air inlet and the motor chamber.

In some embodiments, the air cooling structure includes a baffle plate disposed in the housing and closing an opening of the buffer chamber facing the motor chamber, the baffle plate having a vent opening, the buffer chamber being in communication with the motor chamber through the vent opening.

In some embodiments, the baffle is provided with a plurality of air vents, and the plurality of air vents are uniformly arranged on the baffle at intervals along the circumferential direction of the rotor.

In some embodiments, the air ports are located outside the windings of the stator in the radial direction of the rotor.

In some embodiments, the ratio of the outer diameter of the stator to the number of the air vents is 18-25.

In some embodiments, the air compressor includes a cooling water inlet, a cooling water outlet and a spiral flow channel, the cooling water inlet, the cooling water outlet and the spiral flow channel are all disposed on the housing, the cooling water inlet and the cooling water outlet are communicated through the spiral flow channel, and the cooling water cools the iron core of the stator when flowing through the spiral flow channel.

In some embodiments, both ends of the spiral flow path extend beyond both side edges of the core in the axial direction of the rotor.

In some embodiments, the ends of the helical flow channels extend 20-30 mm beyond the edge of the core in the axial direction of the rotor.

The second aspect of the present disclosure also provides an air conditioner, which includes the air compressor of the embodiment of the present disclosure.

The third aspect of the present disclosure also provides an automobile, which includes the air compressor of the embodiment of the present disclosure.

The radial bearing is provided with the bearing air cooling flow passage, so that cooling air can flow through the inner part of the radial bearing, and the cooling effect of the radial bearing in the air compressor is favorably improved.

Other features of the present disclosure and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.

Drawings

In order to more clearly illustrate the embodiments of the present disclosure or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly introduced below, it is obvious that the drawings in the following description are only some embodiments of the present disclosure, and for those skilled in the art, other drawings can be obtained according to the drawings without inventive exercise.

Fig. 1 is a schematic structural diagram of an air compressor in the embodiment of the present disclosure.

Fig. 2 is a schematic gas path diagram of an air cooling structure according to an embodiment of the disclosure.

FIG. 3 is a schematic view of the arrangement of the first axial flow passage and the vent in an embodiment of the present disclosure.

Fig. 4 is a schematic layout of a first radial flow passage in an embodiment of the present disclosure.

FIG. 5 is a schematic layout of a second axial flow passage and a second radial flow passage in an embodiment of the present disclosure.

Description of reference numerals:

10. an air compressor;

11. a housing; 12. a first seal plate; 13. a second seal plate; 14. a motor cavity; 15. a bearing cavity;

2. a motor; 21. a stator; 211. an iron core; 212. a winding; 22. a rotor; 23. a first impeller; 24. a second impeller;

3. a radial bearing; 31. a first radial bearing; 32. a second radial bearing; 33. a bearing housing;

4. a bearing seat; 41. a first bearing housing; 42. a second bearing housing; 43. mounting holes;

5. an axial bearing; 51. a first axial bearing; 52. a second axial bearing;

6. an air-cooled structure; 61. a cooling gas inlet; 62. a cooling gas outlet; 63. a bearing air-cooling flow passage; 631. a first bearing runner; 632. a second bearing runner; 633. a first radial flow passage; 634. a first axial flow passage; 635. a second axial flow passage; 636. a second radial flow passage; 64. a flow passage is communicated; 65. a cache cavity; 66. a baffle plate; 661. a vent; 662. connecting holes;

7. a water-cooling structure; 71. a cooling water inlet; 72. a cooling water outlet; 73. a spiral flow channel;

81. a seal ring; 82. a gasket;

Detailed Description

The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the disclosure, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments disclosed herein without any inventive step, are intended to be within the scope of the present disclosure.

Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate.

In the description of the present disclosure, it should be understood that the terms "first", "second", etc. are used to define the components, and are used only for convenience of distinguishing the corresponding 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 disclosure.

In addition, technical features involved in different embodiments of the present disclosure described below may be combined with each other as long as they do not conflict with each other.

Fig. 1-5 exemplarily show the structure of the air compressor of the present disclosure.

Referring to fig. 1, in some embodiments, air compressor 10 is a centrifugal air compressor that includes a housing 11, a motor 2, a compression device, and a bearing device.

The housing 1 is provided with a chamber therein for providing an installation space for the motor 2 and other structural components such as a bearing device. As an example, the housing 1 is cylindrical.

The motor 2 is disposed in the housing 1 and includes a stator 21 and a rotor 22. The stator 21 is fixedly disposed in the housing 1, for example, in some embodiments, the stator 21 is fixed to an inner surface of the housing 1 by interference. The rotor 22 is rotatably disposed in the housing 1 and penetrates the stator 2, i.e., the rotor 3 is rotatably disposed through the stator 21. The stator 21 includes a core 211 and a winding 212. The iron core 211 includes silicon steel sheets, which are stacked. The winding 212 is wound around the core 211, and specifically, as shown in fig. 1, the winding 212 is wound around an inner wall of the core 211 and extends from the core 211 toward two axial sides, so as to form a first coil (for example, one coil located on the right side in fig. 1, which may also be referred to as a right-side coil) and a second coil (for example, one coil located on the left side in fig. 1, which may also be referred to as a left-side coil) located on two axial sides of the core 211.

In the working process, the rotor 22 rotates at a high speed and is matched with the stator 21 to realize the conversion of electric energy and mechanical energy so as to drive the compression device to rotate.

The compressor is used for compressing air and pressurizing the air. The compression device includes an impeller disposed on a rotor 22. For example, referring to fig. 1, in some examples, the compression device includes two impellers, namely a first impeller 23 and a second impeller 24, and the first impeller 23 and the second impeller 24 are respectively connected to two axial ends of the rotor 22 to rotate under the driving of the rotor 22, so as to form a negative pressure, suck air from the outside, make the air flow to the impeller outlet under the centrifugal force, and increase the pressure of the air through the diffusion effect of the impellers and the diffusion channel, thereby achieving the purpose of air pressurization.

The bearing device is disposed on the rotor 22 for supporting the rotor 22. Referring to fig. 1, in some embodiments, the bearing arrangement comprises a radial bearing 3 and the bearing arrangement further comprises an axial bearing 5. As an example, the radial bearing 3 and the axial bearing 5 are both gas bearings, in which case the radial bearing 3 is a radial gas bearing and the axial bearing 5 is an axial gas bearing. The gas bearing works by utilizing gas, does not need to be lubricated by lubricating oil, and has the advantages of low friction resistance, wide application speed range and temperature range and the like.

With continued reference to fig. 1, in some embodiments, the bearing arrangement comprises at least two radial bearings 3. For example, as can be seen from fig. 1, in some embodiments, the bearing arrangement comprises two radial bearings 3, a first radial bearing 31 and a second radial bearing 32. The first radial bearing 31 and the second radial bearing 32 are provided at both axial ends of the rotor 22 and are located at both axial sides of the stator 21. Bearing blocks 4 are respectively sleeved outside the two radial bearings 3, and the radial bearings 3 are supported by the bearing blocks 4. As an example, referring to fig. 3, the bearing seat 4 is provided with a mounting hole 43, and during assembly, a threaded connector such as a screw is inserted through the mounting hole 43 to fix the bearing seat 4 to the housing 11. The bearing housing 4 corresponding to the first radial bearing 31 is referred to as a first bearing housing 41, and the first bearing housing 41 supports the first radial bearing 31. The bearing housing 4 corresponding to the second radial bearing 32 is referred to as a second bearing housing 42, and the second bearing housing 42 supports the second radial bearing 32. As shown in fig. 1 and 2, a portion of the first bearing seat 41 protrudes outside the housing 11 and is in sealing engagement with the first axial end surface of the housing 11 via a seal ring 81 (see fig. 2, which may be an O-ring). The second bearing housing 42 is located entirely inside the housing 11 and engages with the inner wall of the housing 11. Meanwhile, the first and second seal plates 12 and 13 are provided axially outside the first and second bearing housings 41 and 42, respectively. The first cover plate 12 is located between the first impeller 23 and the first radial bearing 31 and the first bearing seat 41, as shown in fig. 1, and in some embodiments, the first cover plate 12 and the first bearing seat 41 are sealed by a sealing ring 81. The second closing plate 13 is located between the second impeller 24 and the second radial bearing 32, and the second closing plate 13 is fitted to the second axial end surface of the casing 11 to close the space inside the casing 11 located axially outside the second bearing housing 42.

As shown in fig. 1, the chamber in the housing 11 is partitioned into the motor chamber 14 and the bearing chamber 15 by the partitioning action of the first bearing housing 41, the second bearing housing 42, and the like. The motor cavity 14 is located between the housing 11, the first bearing housing 41 and the second bearing housing 42. The motor cavity 14 is a space where the motor 2 is located, the stator 21 is located in the motor cavity 14, and the rotor 22 penetrates out of the motor cavity 14. The bearing cavity 15 is located between the second bearing housing 42, the second closure plate 13, the rotor 22 and the housing 11.

Further, referring to fig. 1, in some embodiments, the bearing arrangement comprises at least two axial bearings 5. For example, as can be seen from fig. 1, in some embodiments, the bearing arrangement comprises two axial bearings 5, respectively a first axial bearing 51 and a second axial bearing 52. The first axial bearing 51 and the second axial bearing 52 are both located in the bearing cavity 15, and in this case, the first axial bearing 51 and the second axial bearing 52 are both located on the side of the second radial bearing 32 away from the stator 21 (also on the side of the second radial bearing 32 away from the first radial bearing 31). The first axial bearing 51 and the second axial bearing 52 are arranged in this order in a direction away from the stator 21, that is, the first axial bearing 51 is close to the stator 21 with respect to the second axial bearing 52.

During the operation of the air compressor 10, the stator 21, the rotor 22, the bearing device and the like generate heat, and if the heat is not effectively cooled, the performance is easily deteriorated, the service life is shortened, and the operation precision, the working reliability and the service life of the air compressor 10 are affected. For example, the rotor 22 is affected by the frequency conversion harmonic wave, and the magnetic steel position thereof is extremely easy to exceed the tolerance temperature of the magnetic steel, so that demagnetization is generated. For another example, if the core 211 and the winding 212 of the stator 21 cannot be cooled effectively, the life and performance of the stator 21 are affected. The life and performance of the radial bearing 3 and the axial bearing 5 are also affected if the radial bearing 3 and the axial bearing 5 are not cooled effectively.

Therefore, the air compressor 10 needs to be cooled to prevent overheating of the structural components of the air compressor 10, which affects the service life and performance stability.

The radial bearing 3 is cooled by an air cooling method in general. However, in the related art, the cooling air generally flows only through the surface of the radial bearing 3, for example, through the gap between the radial bearing 3 and the rotor 22, in which case the cooling air cannot sufficiently remove the heat of the radial bearing 3, and the cooling effect is to be improved.

In view of the above, referring to fig. 2, in some embodiments of the present disclosure, the air compressor 10 includes an air cooling structure 6, and the air cooling structure 6 includes a cooling air inlet 61, a cooling air outlet 62, and a bearing air cooling flow passage 63. The cooling air inlet 61 and the cooling air outlet 62 are both disposed on the housing 11, and specifically, the cooling air inlet 61 and the cooling air outlet 62 are both disposed on a side wall of the housing 11 and communicate with a chamber in the housing 11. The bearing air cooling flow passage 63 is provided on the radial bearing 3, for example, referring to fig. 4, in some embodiments, the bearing air cooling flow passage 63 is provided on the bearing housing 33 of the radial bearing 3 inside the bearing housing 33. The bearing air cooling flow passage 63 communicates with the cooling air inlet 61 and the cooling air outlet 62.

Based on the above arrangement, the cooling air can flow through the bearing air cooling flow passage 63 in the process of flowing from the cooling air inlet 61 to the cooling air outlet 62, and since the bearing air cooling flow passage 63 is arranged on the radial bearing 3, the cooling air flowing through the bearing air cooling flow passage 63 actually flows through the radial bearing 3, so that compared with the case that the cooling air only flows through the surface of the radial bearing 3 and does not flow through the inside of the radial bearing 3, the heat of the radial bearing 3 can be more sufficiently taken away, the radial bearing 3 is more sufficiently cooled, the service life of the radial bearing 3 is prolonged, the operation stability and the working reliability of the air compressor 10 are further improved, and the service life of the air compressor 10 is prolonged.

As an example, referring to fig. 2, in the case where the air compressor 10 includes the first radial bearing 31 and the second radial bearing 32, the cooling air inlet 61 and the cooling air outlet 62 are sequentially arranged in a direction from the first radial bearing 31 to the second radial bearing 32, that is, the first radial bearing 31 and the second radial bearing 32 are sequentially arranged in a direction from the cooling air inlet 61 to the cooling air outlet 62, and the bearing air cooling flow passage 63 includes a first bearing flow passage 631 and a second bearing flow passage 632, the first bearing flow passage 631 being provided on the first radial bearing 31, the second bearing flow passage 632 being provided on the second radial bearing 32, the first bearing flow passage 631 and the second bearing flow passage 632 both communicating with the motor cavity 14. In this way, the cooling air flowing into the housing 11 from the cooling air inlet 61 can flow through the first bearing flow channel 631 of the first radial bearing 31 and the second bearing flow channel 632 of the second radial bearing 32 in sequence in the process of flowing to the cooling air outlet 62, so as to cool the first radial bearing 31 and the second radial bearing 32 in sequence. Since the cooling air can flow through the inside of the first and second radial bearings 31 and 32, it is possible to achieve more sufficient cooling of the first and second radial bearings 31 and 32.

As an embodiment of first bearing runner 631, referring to FIG. 2, first bearing runner 631 includes a first radial runner 633 and a first axial runner 634. The first radial flow path 633 extends in the radial direction of the rotor 22 (also in the radial direction of the first radial bearing 31). The first axial flow passage 634 extends in the axial direction of the rotor 22 (also in the axial direction of the first radial bearing 31). The first radial flow passage 633 is communicated with the cooling air inlet 61 and communicated with the motor cavity 14 through a first axial flow passage 634, for example, referring to fig. 2, in some embodiments, a communication flow passage 64 is provided on the first bearing seat 41, and the first radial flow passage 633 is communicated with the cooling air inlet 61 through the communication flow passage 64 on the first bearing seat 41, so that the bearing air cooling flow passage 63 is communicated with the cooling air inlet 61 through the communication flow passage 64 on the bearing seat 4. Based on this, when flowing through the interior of the first radial bearing 31, the cooling air flowing in from the cooling air inlet 61 may first enter the first radial flow passage 633, flow in the radial direction, then flow from the first radial flow passage 633 into the first axial flow passage 634, flow in the axial direction, then flow out from the first axial flow passage 634, flow into the motor cavity 14, and continue flowing downstream. The flow mode of firstly radial and then axial is more in accordance with the characteristic of the relative position relationship between the first radial bearing 31 and the cooling air inlet 61, the flow path is shorter, and the cooling effect is better.

Referring to fig. 3 and 4, the number of the first radial flow passages 633, the first axial flow passages 634, and the communication flow passages 64 on the first bearing block 41 is not limited to one. For example, as shown in fig. 3 and fig. 4, in some embodiments, a plurality of first radial runners 633 and a plurality of first axial runners 634 are disposed on the first radial bearing 31, and the plurality of first radial runners 633 and the plurality of first axial runners 634 are uniformly distributed along the circumferential direction. Since the number of the first radial runners 633 and the first axial runners 634 is large and the distribution is uniform, the first radial bearing 31 can be cooled more sufficiently and uniformly, and the first radial bearing 31 can be prevented from forming a local high temperature region due to local non-cooling. In addition, in some embodiments, a plurality of (for example, 4) communication flow passages 64 are provided on the first bearing seat 41, and the plurality of communication flow passages 64 are uniformly distributed on the first bearing seat 41 along the circumferential direction and are in one-to-one correspondence with the first radial flow passages 633, so that the cooling air can enter the first radial bearing 31 more uniformly to uniformly cool the first radial bearing 31.

As an embodiment of second bearing runner 632, referring to FIG. 2, second bearing runner 632 includes a second axial runner 635 and a second radial runner 636. The second axial flow passage 635 extends in the axial direction of the rotor 22 (also in the axial direction of the second radial bearing 32). The second radial flow passage 636 extends in the radial direction of the rotor 22 (also in the radial direction of the second radial bearing 32). The second axial flow passage 635 is in communication with the motor cavity 14 and is in communication with the cooling air outlet 62 through a second radial flow passage 636, for example, referring to fig. 2 and 5, in some embodiments, a communication flow passage 64 is provided on the second bearing housing 42, and the second radial flow passage 636 is in communication with the cooling air outlet 62 through the communication flow passage 64 on the second bearing housing 42, so that the bearing air cooling flow passage 63 can be in communication with the cooling air outlet 62 through the communication flow passage 64 on the bearing housing 4. In this regard, the cooling air may first enter the second axial flow passage 635, flow axially, then flow from the second axial flow passage 635 into the second radial flow passage 636, flow radially, and then flow out of the second radial flow passage 636 to continue flowing downstream when flowing through the interior of the second radial bearing 32. The flow mode of firstly axial and then radial is more in line with the relative position relation characteristics between the second radial bearing 32 and the first radial bearing 31, between the motor cavity 14 and between the cooling air outlet 62, and the flow path is shorter and the cooling effect is better.

Referring to fig. 5, the numbers of the second axial flow passage 635, the second radial flow passage 636 and the communication flow passage 64 on the second bearing housing 42 are not limited to one. For example, as shown in fig. 5, in some embodiments, a plurality of second axial flow passages 635 and a plurality of second radial flow passages 636 are provided on the first radial bearing 31, and the plurality of second axial flow passages 635 and the plurality of second radial flow passages 636 are all uniformly distributed along the circumferential direction. Because the second axial flow passages 635 and the second radial flow passages 636 are more in number and are uniformly distributed, the second radial bearing 32 can be more sufficiently and uniformly cooled, and the second radial bearing 32 can be prevented from forming a local high-temperature region due to local non-cooling. In addition, referring to fig. 5, in some embodiments, a plurality of (e.g., 4) communication flow passages 64 are provided on the second bearing seat 42, and the plurality of communication flow passages 64 are uniformly distributed on the second bearing seat 42 along the circumferential direction and are in one-to-one correspondence with the second radial flow passages 636, so that the cooling air flowing out from the second radial bearing 32 can flow downstream more uniformly, and uniform cooling of the downstream component (e.g., the axial bearing 5) is achieved.

Referring to fig. 2, in the case that the bearing device includes the axial bearing 5 at the same time, in some embodiments, the second radial flow passage 636 communicates with the cooling air outlet 62 through the space where the axial bearing 5 is located (i.e., the bearing cavity 15), so that the second bearing flow passage 632 communicates with the cooling air outlet 62 through the space where the axial bearing 5 is located, so that the cooling air flowing out of the second bearing flow passage 632 can flow through the axial bearing 5 in the process of flowing to the cooling air outlet 62, and cool the axial bearing 5, and thus the first radial bearing 31, the second radial bearing 32, and the axial bearing 5 (e.g., the first axial bearing 51 and the second axial bearing 52) are sequentially cooled.

As a further improvement to the foregoing embodiments, referring to fig. 2, the air cooling structure 6 includes a buffer chamber 65, and the buffer chamber 65 is located in the housing 11 and communicates with the cooling air inlet 61 and the bearing air cooling flow passage 63. Specifically, as shown in fig. 2, in the embodiment in which the air compressor 10 includes the first radial bearing 31 and the second radial bearing 32, the buffer chamber 65 is located upstream of the first radial bearing 31, that is, upstream of the first bearing flow passage 631. More specifically, as shown in fig. 2, when the first bearing flow passage 631 includes a first radial flow passage 633 and a first axial flow passage 634, the buffer chamber 65 is located upstream of the first radial flow passage 633, and is specifically disposed on the first bearing seat 41, and is a complete annular groove on the first bearing seat 41, and is located upstream of the communication flow passage 64 of the first bearing seat 41.

With the above arrangement, the cooling air flowing from the cooling air inlet 61 to the inside of the housing 1 flows into the buffer chamber 65 first and then flows toward the bearing air cooling flow passage 63. In the case where the buffer chamber 65 is not provided, since the air pressure on the side close to the cooling air inlet 61 is generally larger and the air pressure on the side far from the cooling air inlet 61 is generally smaller in the radial direction, the air flow on the side close to the cooling air inlet 61 may be larger and the air flow on the side far from the cooling air inlet 61 may be smaller, which may cause uneven cooling, and the cooling on the side close to the cooling air inlet 61 may be more sufficient and the cooling on the side far from the cooling air inlet 61 may be worse. And set up buffer memory chamber 65 after, buffer memory chamber 65 can carry out the buffer memory to the cooling gas, makes atmospheric pressure distribute more evenly, prevents to be close to cooling gas inlet 61 one side and keeps away from the atmospheric pressure difference of cooling gas inlet 61 one side too big, and the guide cooling gas is more fully distributed in whole footpath, consequently, can effectively improve the cooling homogeneity, realizes the even cooling to the radial different positions of each part (for example radial bearing 3, stator 21 and rotor 22) in the casing 11.

Further, referring to FIG. 2, in some embodiments, the buffer chamber 65 communicates not only with the cooling air inlet 61 and the bearing air cooling channel 63, but also with the cooling air inlet 61 and the motor chamber 14. Based on this, as shown in fig. 2, the cooling air flowing from the cooling air inlet 61 into the buffer cavity 65 may flow downstream in two paths, wherein one path directly flows to the motor cavity 14, flows through the space between the stator 21 and the housing 11 and between the stator 21 and the rotor 22 to cool the stator 21 and the rotor 22 in the motor cavity 14, and the other path first flows to the radial bearing 3 to cool the radial bearing 3, and then flows to the motor cavity 14 to flow through the space between the stator 21 and the housing 11 and between the stator 21 and the rotor 22 to cool the stator 21 and the rotor 22 in the motor cavity 14, so that the radial bearing 3, the stator 21, and the rotor 22 can be cooled more effectively. Due to the buffer pressure equalizing effect of the buffer chamber 65, the cooling gas can cool more uniformly not only different radial portions of the radial bearing 3, but also different radial portions of the stator 21 and the rotor 22.

Wherein, as an implementation manner of realizing that cache chamber 65 and motor chamber 14 communicate, see fig. 2, air cooling structure 6 includes baffle 66, and baffle 66 sets up in casing 11 and seals the opening towards motor chamber 14 of cache chamber 65 to, be equipped with vent 661 on baffle 66, cache chamber 65 passes through vent 661 and motor chamber 14 communicates. Specifically, referring to fig. 3, in some embodiments, the baffle plate 66 is a circular ring plate that is fitted over the first bearing seat 41 and has a connecting hole 662, and a screw or other threaded connecting member passes through the connecting hole 662 to fix the baffle plate 66 to the housing 11. Further, as shown in fig. 2, a gasket 82 is provided between the baffle plate 66 and the first bearing housing 41 to improve the sealing property.

Set up baffle 66 to realize the intercommunication between buffer memory chamber 65 and the motor chamber 14 through vent 661 on baffle 66, on the one hand can make the cooling gas in buffer memory chamber 65 directly flow to the motor chamber 14 in, on the other hand also can prevent that the cooling gas in buffer memory chamber 65 is whole to rush to the motor chamber 14 in the twinkling of an eye, guide cooling gas when flowing to motor chamber 14, also flow to journal bearing 3, effective control cooling gas flow is in the distribution between motor chamber 14 and journal bearing 3.

The number of the vent holes 661 is not limited. For example, referring to fig. 3 and 4, in some embodiments, the number of vents 661 can be multiple. For example, the ratio of the outer diameter of the stator 21 to the number of the vent holes 661 is 18 to 25.

To further improve the uniformity of cooling of stator 21 and rotor 22, referring to fig. 3 and 4, in some embodiments, air ports 661 on baffle 66 are evenly spaced on baffle 66 along the circumference of rotor 22 (and also the circumference of baffle 66). In this way, the cooling air in the buffer chamber 65 can flow into the motor chamber 14 more uniformly, and the stator 21 and the rotor 22 are cooled more uniformly, so that better cooling uniformity is achieved, and local high temperature is prevented.

In addition, referring to fig. 2, in some embodiments, vent 661 is located outside winding 212 of stator 21 in a radial direction of rotor 22, that is, vent 661 is located radially outside winding 212 of stator 21. As shown in fig. 2, after the gas flows out through vent holes 661, the gas is blown to winding 212 to cool the corresponding side wire package, thereby achieving sufficient cooling of the corresponding side wire package. It will be seen that this arrangement allows for specific cooling of the coil on the side of the baffle 66 (the right coil in figure 1) in a targeted manner, which improves the cooling of the coil over that which would be the case in the related art without specific cooling of the coil. Especially, when vent 661 evenly distributes along circumference, can realize the even ring blow to the side solenoid that baffle 66 is located, evenly cool down to corresponding side solenoid. The effective cooling of the coil is beneficial to prolonging the service life of the stator 21 and improving the working reliability of the stator 21.

In the above embodiments, the radial bearing 3, the axial bearing 5, the stator 21, and the rotor 22 are all cooled by air cooling.

Instead of cooling the air compressor 10 by air cooling, the air compressor 10 may be cooled by water cooling.

Returning to fig. 1, as an implementation manner of the water cooling manner, the air compressor 10 includes a water cooling structure 7, the water cooling structure 7 includes a cooling water inlet 71, a cooling water outlet 72, and a spiral flow channel 73, the cooling water inlet 71, the cooling water outlet 72, and the spiral flow channel 73 are all disposed on the housing 11, the cooling water inlet 71 and the cooling water outlet 72 are communicated through the spiral flow channel 73, and the cooling water cools the iron core 211 of the stator 21 when flowing through the spiral flow channel 73. Specifically, the spiral flow path 73 is located inside the housing 11. Thus, the core 211 of the stator 21 can be cooled by a water cooling method, the temperature of the silicon steel plate of the stator 21 can be reduced, and the service life of the stator 21 can be prolonged.

As shown in fig. 1, in some embodiments, both ends of the spiral flow channel 73 extend beyond both side edges of the core 211 of the stator 21 in the axial direction of the rotor 22, for example, the ends of the spiral flow channel 73 extend 20 to 30mm beyond the edges of the core 211 in the axial direction of the rotor 22.

In the above arrangement, since the two axial ends of the spiral flow channel 73 extend axially outward with respect to the two axial ends of the core 211 of the stator 21, the spiral flow channel 73 can completely cover the core 211 of the stator 21, and thus the silicon steel sheet of the stator 21 can be more sufficiently water-cooled.

Referring to fig. 1 and 2, when the air compressor 10 includes the air cooling structure 6 and the water cooling structure 7 of each of the foregoing embodiments, the air compressor 10 may be cooled by a combined cooling method of air cooling and water cooling coupling, so as to implement a combined type intensive cooling process for the air compressor 10, effectively overcome limitations of using a water cooling or air cooling method alone, and more fully and effectively reduce the temperatures of the radial bearing 3, the axial bearing 5, the stator 21, and the rotor 22.

The composite forced cooling process described above is described next with reference to the embodiments shown in fig. 1-5.

It is to be understood that in the following description, directional terms such as "front, back, up, down, left, right", "lateral", "vertical, horizontal" and "top, bottom" generally refer to the orientation or positional relationship shown in fig. 1, merely to facilitate the description of the disclosure and to simplify the description, and that these directional terms are not intended to indicate and imply that the apparatus or component being referred to must have a particular orientation or be constructed and operated in a particular orientation without having to be otherwise specified, and therefore should not be considered as limiting the scope of the disclosure; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.

As shown in fig. 1 to 5, in the illustrated embodiment, the air compressor 10 includes a housing 11, a stator 21, a rotor 22, a first radial bearing 31, a first bearing housing 41, a second radial bearing 32, a second bearing housing 42, a first axial bearing 51, a second axial bearing 52, a first closing plate 12, a second closing plate 13, and a baffle 66.

As shown in fig. 1 and 2, in this embodiment, a first radial bearing 31 and a second radial bearing 32 are provided on the rotor 22 and are located on the right and left sides of the stator 21, respectively. The first bearing housing 41 and the second bearing housing 42 are supported between the first radial bearing 31 and the second radial bearing 32, respectively, and the housing 11. The spaces between the first bearing housing 41, the second bearing housing 42 and the housing 11 form the motor cavity 14. The first cover plate 12 is located to the right of the first bearing housing 41. The second closing plate 13 is located on the left side of the second bearing housing 42. The space between the second bearing housing 42, the second closing plate 13, the housing 11 and the rotor 22 forms a bearing cavity 15, and the first axial bearing 51 and the second axial bearing 52 are both provided in the bearing cavity 15 and are arranged in this order from right to left.

As shown in fig. 1 and 2, in this embodiment, the housing 11 is provided with a cooling water inlet 71, a cooling water outlet 72, a spiral flow passage 73, a cooling air inlet 61, and a cooling air outlet 62. The cooling water inlet 71 and the cooling air outlet 62 are both located on the left side of the stator 21. The cooling water outlet 72 and the cooling air inlet 61 are both located on the right side of the stator 21. Between two of the cooling water inlet 71, the cooling water outlet 72, the cooling air inlet 61 and the cooling air outlet 62, they may be located on the same plane of the housing 11, or may be arranged at an angle. The spiral flow channel 73 is communicated with the cooling water inlet 71 and the cooling water outlet 72, the left and right width of the spiral flow channel is wider than the left and right width of the iron core 211 of the stator 21, and the flow area of the spiral flow channel is 30-40 mm²。

As shown in fig. 2 to 4, in this embodiment, the first bearing housing 41 is provided with a buffer chamber 65 and four communication flow passages 64. The buffer chamber 65 is a recess open to the right. The four communication flow passages 64 on the first bearing block 41 are uniformly distributed in the circumferential direction, and each communication flow passage 64 extends in the radial direction and communicates the buffer chamber 65 and the first radial bearing 31.

As shown in fig. 2, a baffle 66 is provided at the opening of the buffer chamber 65 toward the right (i.e., the opening toward the motor chamber 14). The baffle 66 blocks the opening of the buffer chamber 65, and as shown in fig. 2 to 4, the baffle 66 is provided with a plurality of vent holes 661 uniformly distributed along the circumferential direction, and the vent holes 661 are located on the radial outer side of the right side coil of the stator 21 to communicate the buffer chamber 65 with the motor chamber 14. Compared with the situation that the buffer cavity 65, the baffle 66 and the cooling air inlet 61 are arranged on the left side, the buffer cavity 65, the baffle 66 and the cooling air inlet 61 are arranged on the right side, so that the space on the right side is relatively large, the buffer cavity 65 is more conveniently arranged, and the buffer cavity 65 can be more conveniently and fully utilized to realize air equalization.

As shown in fig. 2 to 4, in this embodiment, four first radial runners 633 and a plurality of first axial runners 634 are provided on the first radial bearing 31 and are evenly distributed in the circumferential direction. Each first radial flow passage 633 communicates with each communication flow passage 64 on the first bearing housing 41, and communicates with an inlet of the first axial flow passage 634. The outlet of each first axial flow passage 634 is in communication with the motor chamber 14.

As shown in fig. 5, in this embodiment, the second radial bearing 32 is provided with a plurality of second axial flow passages 635 and four second radial flow passages 636 which are uniformly distributed in the circumferential direction. The inlet of each second axial flow passage 635 communicates with the motor cavity 14. Meanwhile, the outlet of the second axial flow passage 635 communicates with the second bearing housing 42 through each second radial flow passage 636.

As shown in fig. 5, in this embodiment, four communication flow passages 64 are provided on the second bearing block 42 and are uniformly distributed in the circumferential direction. Each communication flow passage 64 of the second bearing housing 42 extends in the radial direction and communicates each second radial flow passage 636 with the bearing chamber 15.

As shown in fig. 5 and 2, the bearing chamber 15 communicates with the cooling air outlet 62.

Based on the above arrangement, this embodiment can realize both the water-cooling process and the air-cooling process.

Wherein, the water-cooling process is as follows: the cooling water enters the housing 11 through the cooling water inlet 71, flows through the spiral flow channel 73, carries away heat of the housing 11 and the silicon steel sheets of the stator 21, and then flows out through the cooling water outlet 72.

As shown by the arrows in fig. 2, the air cooling process is:

firstly, cooling air enters the housing 11 through the cooling air inlet 61, flows through the communication flow passage 64 arranged above the first bearing seat 41, and then enters the buffer chamber 65 arranged on the first bearing seat 41;

then, the gas entering the buffer chamber 65 is divided into two parts when continuing to flow downstream, wherein one part of the gas is directly blown to the right side coil of the stator 21 through vent holes 661 uniformly distributed on the baffle plate 66 in 360 degrees, so as to uniformly and circularly blow the right side coil, and fully and uniformly cool the right side coil; another part of the air flows through the first radial flow passages 633 on the first radial bearing 31 through the communication flow passages 64 arranged above the first bearing seat 41 and flows to the first axial flow passages 634 on the first radial bearing 31, in the process, the part of the air is also collected and brings the air in the space between the first bearing seat 41 and the first closing plate 12 to fully flow, and the cooling air fully takes away the heat of the first radial bearing 31 in the process of flowing through the first radial bearing 31, and of course, in the process, a part of the cooling air flows into the gap between the first radial bearing 31 and the rotor 22 to be cooled;

after the cooling of the right-side coil and the first radial bearing is respectively completed, the two parts of gas are collected at a gap between the stator 21 and the rotor 22, and heat generated by the rotor 22 due to harmonic heating and wind mill loss is continuously taken away through gas convection to cool the rotor 22;

after the cooling air flows out from the gap between the stator 21 and the rotor 22, a part of the cooling air flows towards the radial outer side, flows through the left side coil of the stator 21 to take away the heat of the left side coil, then collects the other part of the cooling air, flows through the second radial bearing 32 together, sequentially flows through the second axial flow passage 635 and the second radial flow passage 636 on the second radial bearing 32 to take away the heat of the second radial bearing 32;

then, all the cooling air flows out from the second radial flow passage 636 and reaches the bearing cavity 15, and the heat of the first axial bearing 51 and the second axial bearing 52 is sufficiently taken away by driving the air in the bearing cavity 15 to flow;

finally, the heat-absorbed gas flows to the outside of the case through the cooling gas outlet 62.

It can be seen that, in this embodiment, the air compressor 10 is cooled by a water-cooling and air-cooling combined enhanced cooling method, which not only can effectively cool the silicon steel plate of the stator 21, but also can sufficiently and uniformly air-cool the coils on both sides of the stator 21 and the rotor 22, and can uniformly blow and uniformly cool the coils on both sides, and also can perform relatively precise cooling air management on two radial bearings and two axial bearings, thereby effectively cooling each bearing. Like this, be favorable to improving the operation precision and the operational reliability of air compressor machine 10, prolong the life of air compressor machine 10.

The air compressor 10 of this embodiment may be applied to various air-using systems, for example, may be applied to an air supply system of a fuel cell engine of an automobile (e.g., an electric automobile) or the like, or may also be applied to an air conditioner.

The above description is only exemplary of the present disclosure and is not intended to limit the present disclosure, and any modification, equivalent replacement, or improvement made within the spirit and principle of the present disclosure should be included in the scope of the present disclosure.

Claims (17)

1. An air compressor (10), comprising:

a shell (11) which is internally provided with a motor cavity (14);

a motor (2) disposed in the motor cavity (14) and including a stator (21) and a rotor (22), the rotor (22) passing through the stator (21);

a radial bearing (3) arranged on the rotor (22); and

the air cooling structure (6) comprises a cooling air inlet (61), a cooling air outlet (62) and a bearing air cooling flow channel (63), wherein the cooling air inlet (61) and the cooling air outlet (62) are arranged on the shell (11), and the bearing air cooling flow channel (63) is arranged on the radial bearing (3) and communicated with the cooling air inlet (61) and the cooling air outlet (62).

2. Air compressor (10) according to claim 1, characterized in that said air compressor (10) comprises at least two of said radial bearings (3), the at least two radial bearings (3) comprise a first radial bearing (31) and a second radial bearing (32), the first radial bearing (31) and the second radial bearing (32) are located on both axial sides of the stator (21) and arranged in order in a direction from the cooling air inlet (61) to the cooling air outlet (62), the bearing air cooling flow passage (63) comprises a first bearing flow passage (631) and a second bearing flow passage (632), the first bearing channel (631) is arranged on the first radial bearing (31), the second bearing runner (632) is arranged on the second radial bearing (32), the first bearing runner (631) and the second bearing runner (632) are both in communication with the motor cavity (14).

3. The air compressor (10) of claim 2, wherein the first bearing runner (631) includes a first radial runner (633) and a first axial runner (634), the first radial runner (633) extending in a radial direction of the rotor (22), the first axial runner (634) extending in an axial direction of the rotor (22), the first radial runner (633) communicating with the cooling air inlet (61) and with the motor cavity (14) through the first axial runner (634); and/or the second bearing runner (632) comprises a second axial runner (635) and a second radial runner (636), the second axial runner (635) extends along the axial direction of the rotor (22), the second radial runner (636) extends along the radial direction of the rotor (22), and the second axial runner (635) is communicated with the motor cavity (14) and is communicated with the cooling air outlet (62) through the second radial runner (636).

4. The air compressor (10) according to claim 2, wherein the air compressor (10) comprises an axial bearing (5), the axial bearing (5) is disposed in the housing (11) and located on a side of the second radial bearing (32) away from the first radial bearing (31), and the second bearing flow channel (632) is communicated with the cooling air outlet (62) through a space where the axial bearing (5) is located, so that the cooling air flowing out of the second bearing flow channel (632) flows through the axial bearing (5) in a process of flowing to the cooling air outlet (62) to cool the axial bearing (5).

5. The air compressor (10) according to claim 1, wherein the air compressor (10) comprises a bearing seat (4), the bearing seat (4) supports the radial bearing (3), a communication flow channel (64) is provided on the bearing seat (4), and the cooling air inlet (61) and/or the cooling air outlet (62) are/is communicated with the bearing air cooling flow channel (63) through the communication flow channel (64).

6. Air compressor (10) according to claim 1, characterized in that the bearing air cooling channel (63) is provided on the bearing housing (33) of the radial bearing (3).

7. The air compressor (10) according to any one of claims 1-6, wherein the air cooling structure (6) comprises a buffer chamber (65), the buffer chamber (65) being located inside the housing (11) and communicating the cooling air inlet (61) and the bearing air cooling channel (63).

8. The air compressor (10) of claim 7, wherein the buffer chamber (65) communicates the cooling air inlet (61) and the motor chamber (14).

9. The air compressor (10) according to claim 8, wherein the air cooling structure (6) comprises a baffle plate (66), the baffle plate (66) is disposed in the housing (11) and closes an opening of the buffer chamber (65) facing the motor chamber (14), a vent hole (661) is disposed on the baffle plate (66), and the buffer chamber (65) is communicated with the motor chamber (14) through the vent hole (661).

10. The air compressor (10) of claim 9, wherein the baffle (66) is provided with a plurality of the vent holes (661), and the vent holes (661) are uniformly arranged on the baffle (66) at intervals along a circumferential direction of the rotor (22).

11. Air compressor (10) according to claim 9, characterized in that said ventilation openings (661) are located outside the windings (212) of the stator (21) in the radial direction of the rotor (22).

12. The air compressor (10) of claim 9, wherein the ratio of the outer diameter of the stator (21) to the number of the vent holes (661) is 18-25.

13. The air compressor (10) according to any one of claims 1-6, wherein the air compressor (10) comprises a cooling water inlet (71), a cooling water outlet (72) and a spiral flow channel (73), the cooling water inlet (71), the cooling water outlet (72) and the spiral flow channel (73) are all arranged on the housing (11), the cooling water inlet (71) and the cooling water outlet (72) are communicated through the spiral flow channel (73), and cooling water cools the iron core (211) of the stator (21) when flowing through the spiral flow channel (73).

14. The air compressor (10) according to claim 13, wherein both ends of the spiral flow channel (73) extend beyond both side edges of the iron core (211) in an axial direction of the rotor (22).

15. The air compressor (10) of claim 14, wherein ends of the spiral flow channels (73) extend 20-30 mm beyond edges of the iron core (211) in an axial direction of the rotor (22).

16. An air conditioner, characterized by comprising the air compressor (10) according to any one of claims 1 to 15.

17. An automobile, characterized by comprising an air compressor (10) according to any one of claims 1 to 15.

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