Compressor and air conditioner

Abstract

The invention provides a compressor and an air conditioner, the compressor comprises a bearing, a rotating shaft, a silencer and a rotor, the bearing comprises a main body part and a supporting part, the supporting part is arranged on the main body part, and a first exhaust hole is formed in the main body part. The rotating shaft is connected with the bearing, the silencer is connected with the main body part, a mounting hole and a second exhaust hole are formed in the silencer, the rotating shaft penetrates through the mounting hole and the second exhaust hole to be communicated with the first exhaust hole, the second exhaust hole is formed in the side portion of the silencer, the opening direction of the second exhaust hole deviates from the main body part, and the rotor is located on the side, deviating from the main body part, of the silencer. The rotor sleeves the rotating shaft. According to the scheme, due to the arrangement mode of the second exhaust holes, on the basis that the oil return effect is optimized, the silencer can effectively reduce impact noise of exhaust refrigerants to the rotor, and the vibration and noise reduction function is achieved.

Description

Technical Field

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

[0002] The silent design of compressors is a trend in the industry. Mechanical noise, pneumatic noise, and electromagnetic noise are the main noise sources. To reduce the overall noise level of the compressor and improve the noise quality of the compressor, it is necessary to reduce the exhaust pulsation excitation and reduce the pneumatic noise. The muffler is the core component for reducing the dynamic noise of the refrigerant gas. Therefore, how to optimize the design of the muffler is a problem that needs to be solved currently. Summary of the Invention

[0003] The present invention aims to solve one of the technical problems existing in the prior art or related technologies.

[0004] In view of this, in a first aspect, the present invention provides a compressor, including: a bearing, the bearing includes a main body portion and a support portion, the support portion is provided on the main body portion, and a first exhaust hole is provided on the main body portion; a rotating shaft, connected to the bearing; a muffler, connected to the main body portion, the muffler is provided with a mounting hole and a second exhaust hole, the rotating shaft passes through the mounting hole, the second exhaust hole is communicated with the first exhaust hole, the second exhaust hole is arranged on the side portion of the muffler, and the opening direction of the second exhaust hole faces away from the main body portion; a rotor, the rotor is located on the side of the muffler away from the main body portion, and the rotor is sleeved on the rotating shaft.

[0005] The bearing includes a main body portion and a support portion. The first exhaust hole is formed on the main body portion by machining. The support portion is arranged at the central position of the main body portion and extends along the axial direction of the compressor. The muffler is fixed on the main body portion, and the gas discharged from the first exhaust hole can flow into the muffler. The muffler performs noise reduction processing on the airflow discharged from the first exhaust hole. The rotor is arranged on the side of the muffler away from the main body portion. The rotating shaft is connected to the bearing, and the bearing supports the rotating shaft. The rotating shaft passes through the mounting hole, and a part of the rotating shaft passing through the mounting hole is connected to the rotor, and the rotor is sleeved on the rotating shaft.

[0006] The second exhaust hole is formed on the muffler by machining. The gas flowing into the muffler can be discharged outward through the second exhaust hole. If the second exhaust hole is arranged on the side of the muffler facing the rotor, during the exhaust process, the exhaust will impact the rotating rotor, forming airflow cutting near the rotor, which will increase the exhaust pulsation, affect the exhaust noise, and deteriorate the total value and quality of the compressor noise. If the second exhaust hole is arranged on the side portion of the muffler, and the opening direction of the second exhaust hole is along the radial direction of the compressor, at this time, the exhaust mode is radial exhaust, and at this time, the exhaust is directed at the inner wall surface of the compressor housing. In this exhaust mode, the gas will impact the inner wall surface of the housing, generating a large-range refrigerant gas circulation. The gas circulation will impact the surface of the oil sump, resulting in poor oil return effect and the risk of deteriorating the compressor oil level.

[0007] In this solution, the second exhaust hole is arranged on the side of the muffler, which is equivalent to increasing the distance between the second exhaust hole and the rotor. The gas flowing out of the second exhaust hole gradually diffuses, and the gas discharged from the second exhaust hole is not easy to flow towards the rotor, or only a small amount of gas flows towards the rotor. Therefore, the gas discharged from the second exhaust hole is not easy to impact the rotating rotor, so it is not easy to form airflow cutting near the rotor, reducing the exhaust pulsation, further reducing the exhaust noise, and optimizing the total value and sound quality of the compressor noise.

[0008] In this solution, the opening direction of the second exhaust hole deviates from the main body part. At this time, the exhaust mode is not radial exhaust, and the gas discharged from the second exhaust hole does not directly flow towards the inner wall surface of the compressor housing. In this exhaust mode, the gas is not easy to impact the inner wall surface of the housing, and the gas is not easy to impact the surface of the oil sump, improving the oil return effect.

[0009] It can be seen that in this solution, the setting method of the second exhaust hole can effectively reduce the impact noise of the exhaust refrigerant on the rotor by the muffler on the basis of optimizing the oil return effect, realizing the functions of vibration reduction and noise reduction.

[0010] In some technical solutions, optionally, the muffler includes: a muffler body, with an opening on the side wall of the muffler body; a diversion part, connected to the side wall of the muffler body, and a second exhaust hole is formed between the diversion part and the muffler body, and the second exhaust hole is communicated with the opening.

[0011] An opening is processed on the side wall of the muffler body, and the opening direction of the opening faces the housing of the compressor. In order to avoid the gas impacting the inner wall surface of the compressor housing, a diversion part is arranged outside the muffler body, and a second exhaust hole is formed between the diversion part and the side wall of the muffler body. By setting the diversion part, the flow direction of the gas flowing out of the opening can be changed, so that the gas is not easy to flow towards the inner wall surface of the housing.

[0012] By arranging the diversion part on the muffler body for diversion, it is not necessary to make excessive changes to the shape of the muffler body, thereby reducing the processing difficulty of the muffler.

[0013] In a possible application, the diversion part and the muffler body are of an integral structure, or the diversion part is fixed to the muffler body by welding.

[0014] In some technical solutions, optionally, the side part of the diversion part is parallel to the side wall of the muffler body, or there is an included angle between the side part of the diversion part and the side wall of the muffler body.

[0015] The side of the guide portion can be arranged parallel to the side wall of the muffler body. In this case, the side of the guide portion extends along the axial direction of the compressor, the opening direction of the second exhaust hole is parallel to the axial direction of the compressor, and the gas discharged from the second exhaust hole flows along the axial direction of the compressor. At this time, the gas discharged from the second exhaust hole is not easy to impact the inner wall surface of the shell.

[0016] Alternatively, an angle may be provided between the side portion of the guide portion and the side wall of the muffler body, so that the airflow flowing out of the second exhaust hole is inclined relative to the axial direction of the compressor. In this case, the gas discharged from the second exhaust hole is not easy to impact the inner wall surface of the shell, and the inclined airflow is not easy to impact the rotor, thereby further reducing the exhaust pulsation and thus further reducing the exhaust noise.

[0017] In some technical solutions, optionally, there is an angle α1 between the side of the guide portion and the side wall of the muffler body, and the angle α1 satisfies the following range: 5°<α1<80°.

[0018] There is an angle between the side of the guide part and the side wall of the muffler body. If the angle between the side of the guide part and the side wall of the muffler body is too small, a large amount of airflow will flow directly to the rotor, which may impact the rotor. If the angle between the side of the guide part and the side wall of the muffler body is too large, the airflow discharged from the second exhaust hole may impact the inner wall of the compressor shell. In order to avoid the above situation, the present scheme stipulates that the angle α1 between the side of the guide part and the side wall of the muffler body satisfies the following conditions: 5°<α1<80°. Within this range, the airflow discharged from the second exhaust hole is not easy to impact the rotor and the inner wall of the shell. On the basis of optimizing the oil return effect, the muffler can also effectively reduce the refrigerant gas dynamic noise.

[0019] In some technical solutions, optionally, the muffler body includes multiple protrusions and multiple recesses, and a recess is provided between two adjacent protrusions and a protrusion is provided between two adjacent recesses in the circumference of the muffler body. The number of the guide parts is at least one, and the guide parts are provided on the protrusions and / or recesses.

[0020] A plurality of convex portions and a plurality of concave portions are arranged in the circumferential direction of the muffler body, and the plurality of convex portions and the plurality of concave portions are arranged in sequence and at intervals. In the case where a concave portion is arranged between two convex portions, a connecting hole can be arranged between the two convex portions, and a connecting component is passed through the connecting hole to lock the muffler on the bearing. In this case, the distance between the connecting hole and the center of the muffler is small. If no concave portion is arranged on the muffler body, the connecting hole needs to be arranged on the side of the convex portion away from the center line, resulting in an oversized size of the muffler.

[0021] A guide portion can be provided on at least one of the convex portion and the concave portion. The setting position of the guide portion is relatively flexible. Regardless of whether the guide portion is provided on the convex portion or the concave portion, it can achieve an effective noise reduction effect. The position of the guide portion can be set accordingly according to the layout of the muffler and surrounding components, which is beneficial to improving the rationality of the internal layout of the compressor.

[0022] In some technical schemes, optionally, a rivet hole is provided on the main body, and the compressor also includes a valve plate and a rivet, the rivet is connected to the rivet hole, and the rivet is used to lock the valve plate on the main body; the multiple protrusions include a first protrusion and a second protrusion, and the multiple concave portions include a first concave portion and a second concave portion, along the axial direction of the compressor, the first protrusion faces the first exhaust hole, the second protrusion faces the rivet hole, the first concave portion is located between the first protrusion and the second protrusion, and the second concave portion is located on the side of the second protrusion away from the first concave portion; wherein, a guide portion is provided on at least one of the first protrusion, the second protrusion, the first concave portion and the second concave portion.

[0023] The number of the convex parts is multiple, and two of the convex parts in the multiple convex parts are respectively the first convex part and the second convex part. The number of the concave parts is also multiple, and two of the concave parts in the multiple concave parts are respectively the first concave part and the second concave-convex part. The first convex part, the first concave part, the second convex part and the second concave part are arranged in sequence in the circumferential direction of the muffler body.

[0024] A rivet hole is arranged on the main body, and the rivet passes through the rivet hole, so as to lock the valve plate on the main body. The valve plate is used to open or close the first exhaust hole.

[0025] Along the axial direction of the compressor, the first protrusion faces the first exhaust hole, the second protrusion faces the rivet hole, the first protrusion, the first recess, the second protrusion and the second recess face the exhaust area on the main body. When the guide part is set on any one of the first protrusion, the first recess, the second protrusion and the second recess, the mid- and low-frequency noise can be effectively reduced, which is beneficial to controlling the mid- and low-frequency noise levels.

[0026] In some technical schemes, optionally, the line connecting the center line of the bearing and the center line of the first exhaust hole is L1, and the line L1 extends radially along the bearing; when the guide portion is provided on the first convex portion or the first concave portion, the line connecting the center line of the bearing and the center line of the second exhaust hole is L2, and the line L2 extends radially along the bearing; when the guide portion is provided on the side of the line L1 away from the second convex portion, the angle between the lines L1 and L2 is α2, and α2 is less than 40°; when the guide portion is provided on the side of the line L1 adjacent to the second convex portion or is provided on the first concave portion, the angle between the lines L1 and L2 is α3, and α3 is less than 45°.

[0027] If a guide portion is disposed on the first convex portion or the first concave portion, in order to improve the noise control effect, it is necessary to limit the setting range of the guide portion on the first convex portion or the first concave portion.

[0028] The line connecting the center line of the bearing and the center line of the first exhaust hole is L1, and the line connecting the center line of the bearing and the center line of the second exhaust hole is L2. Both the line L1 and the line L2 extend in the radial direction of the bearing.

[0029] The direction from the first convex portion to the second convex portion is set to be the clockwise direction. Along the clockwise direction, with the line L1 as the reference, the angle between the line L2 and the line L1 is greater than -40° and less than 45°. That is, when the air guide is arranged on the side of the line L1 away from the second convex portion, the angle between the line L1 and the line L2 is less than 40°. When the air guide is arranged on the side of the line L1 adjacent to the second convex portion or on the first concave portion, the angle between the lines L1 and L2 is less than 45°. In the case of this range, the noise of the exhaust gas at the medium and low frequencies can be effectively reduced, which is conducive to controlling the level of the medium and low frequency noise.

[0030] In some technical schemes, optionally, the line connecting the center line of the bearing and the center line of the first exhaust hole is L1, and the line L1 extends along the radial direction of the bearing; when the guide portion is provided on the second convex portion or the second concave portion, the line connecting the center line of the bearing and the center line of the second exhaust hole is L3, and the line L3 extends along the radial direction of the bearing, and the angle between the line L1 and the line L3 is α4, 10°<α4<140°.

[0031] If a guide portion is provided on the second convex portion or the second concave portion, in order to improve the noise control effect, it is necessary to limit the setting range of the guide portion on the second convex portion or the second concave portion.

[0032] The line connecting the center line of the bearing and the center line of the first exhaust hole is L1, and the line connecting the center line of the bearing and the center line of the second exhaust hole is L3.

[0033] The direction from the first convex portion to the second convex portion is set to be clockwise, and the connecting line L1 and the connecting line L2 are sequentially set in the clockwise direction. There is an angle α4 between the connecting line L1 and the connecting line L2, and 10°<α4<140°. Within this range, the exhaust noise in the medium and low frequencies can be effectively reduced, which is beneficial to controlling the medium and low frequency noise levels.

[0034] In some technical solutions, optionally, the rotor and the air guide portion are projected onto the main body, and the projection of the rotor and the projection of the air guide portion are spaced apart from each other.

[0035] The projections of the rotor and the guide part on the main body are spaced from each other, and the projection of the second exhaust hole is located outside the projection of the rotor. Therefore, along the axial direction of the compressor, the guide part and the rotor are staggered, so the second exhaust hole and the rotor are also staggered. Even if the opening direction of the second exhaust hole is parallel to the axial direction of the compressor, the airflow flowing out of the second exhaust hole is not easy to flow directly to the rotor, which can further reduce the impact of the airflow on the rotating shaft, thereby further reducing the exhaust pulsation noise.

[0036] In some technical solutions, optionally, when the number of the second exhaust holes is one, the opening area of the second exhaust hole is S1, the opening area of the first exhaust hole is S2, and 0.4 < S1 / S2 < 1.5; when the number of the second exhaust holes is multiple, the sum of the opening areas of the multiple second exhaust holes is S1, the opening area of the first exhaust hole is S2, and 0.4 < S1 / S2 < 1.5.

[0037] The number of the flow guiding parts can be one or multiple. Therefore, the number of the second exhaust holes can also be one or multiple. When the number of the second exhaust holes is one, the following condition is satisfied between the opening area S1 of the second exhaust hole and the opening area S2 of the first exhaust hole: 0.4 < S1 / S2 < 1.5. In this range, it can ensure that the exhaust smoothly discharges from the second exhaust hole, and moreover, within the above range, the noise during the exhaust process can be reduced, which is beneficial to controlling the medium and low frequency noise level.

[0038] When the number of the second exhaust holes is multiple, the sum of the opening areas of the multiple second exhaust holes is S1, and the following condition is satisfied between S1 and the opening area S2 of the first exhaust hole: 0.4 < S1 / S2 < 1.5. Within this range, it can also ensure that the exhaust smoothly discharges from the second exhaust hole and reduce the noise during the exhaust process.

[0039] In some technical solutions, optionally, the first side of the silencer faces the rotor, and the second exhaust hole is spaced from the first side of the silencer body.

[0040] The first side of the silencer is adjacent to the rotor. Spacing the second exhaust hole from the first side of the silencer body can further move the second exhaust hole away from the rotor, thereby further reducing the impact of the exhaust on the rotor, further reducing the exhaust pulsation, and further reducing the exhaust noise.

[0041] In some technical solutions, optionally, the second side of the silencer faces the main body part. Along the axial direction of the compressor, the distance between the first exhaust hole and the second side of the silencer is H1, and the axial length of the silencer is H2. H1 and H2 satisfy the following condition: 0.2 < H1 / H2 < 0.8.

[0042] The distance between the first exhaust hole and the second side of the silencer is H1, and the overall axial length of the silencer is H2. When the ratio of H1 to H2 is too large, the second exhaust hole is too close to the first side of the silencer, and there is a risk of the exhaust gas flow impacting the rotor. When the ratio of H1 to H2 is too small, the second exhaust hole is too far from the first side of the silencer, and at this time, the installation position of the flow guiding part is limited, resulting in greater processing difficulty of the silencer.

[0043] In this solution, it is defined that H1 and H2 satisfy the following conditions: 0.2 < H1 / H2 < 0.8. Within this range, there is sufficient spacing between the second exhaust hole and the rotor to avoid the exhaust air flow impacting the rotor, and the second exhaust hole is not too far from the first side of the muffler, thus leaving sufficient space for the installation position of the diversion part and facilitating the processing of the muffler.

[0044] In a second aspect, the present invention provides an air conditioner, including the compressor in the first aspect.

[0045] The additional aspects and advantages of the present invention will become apparent in the following description section or be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0046] The above and / or additional aspects and advantages of the present invention will become apparent and be readily understood from the following description of the embodiments in conjunction with the accompanying drawings, in which:

[0047] Figure 1 shows a partial structural schematic diagram of the compressor in an embodiment of the present invention;

[0048] Figure 2 shows a partial structural schematic diagram of the compressor in an embodiment of the present invention;

[0049] Figure 3 shows a partial structural schematic diagram of the compressor in an embodiment of the present invention;

[0050] Figure 4 shows a structural schematic diagram of the muffler in an embodiment of the present invention;

[0051] Figure 5 shows a structural schematic diagram of the muffler in an embodiment of the present invention;

[0052] Figure 6 shows a structural schematic diagram of the muffler in an embodiment of the present invention;

[0053] Figure 7 shows a structural schematic diagram of the muffler in an embodiment of the present invention;

[0054] Figure 8 shows a structural schematic diagram of the muffler in an embodiment of the present invention;

[0055] Figure 9 shows a structural schematic diagram of the muffler in an embodiment of the present invention;

[0056] Figure 10 shows a schematic diagram of the influence of the installation positions of multiple protrusions on the noise transmission loss in an embodiment of the present invention;

[0057] Figure 11Shows a comparison diagram of the axial gas force of the rotor at different setting positions of the second exhaust hole;

[0058] Figure 12 Shows a comparison diagram of the oil quantity in the lower chamber at different setting positions of the second exhaust hole;

[0059] Figure 13 Shows a schematic diagram of the noise spectrum improvement effect of this embodiment.

[0060] Reference numerals:

[0061] 100 Compressor, 110 Bearing, 111 Main body part, 112 Support part, 113 First exhaust hole, 114 Rivet hole, 120 Silencer, 121 Mounting hole, 122 Second exhaust hole, 123 Silencer body, 124 Flow guiding part, 125 Opening, 126 Protrusion, 1261 First protrusion, 1262 Second protrusion, 127 Recess, 1271 First recess, 1272 Second recess, 130 Rotor, 140 Valve plate, 150 Rivet, 160 Rotating shaft. Detailed implementation manners

[0062] In order to more clearly understand the above objects, features and advantages of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific implementation manners. It should be noted that, without conflict, the embodiments of the present application and the features in the embodiments can be combined with each other.

[0063] Many specific details are set forth in the following description in order to fully understand the present invention. However, the present invention can also be implemented in other ways different from those described herein. Therefore, the protection scope of the present invention is not limited by the specific embodiments disclosed below.

[0064] The following refers to Figures 1 to 13 Describe a compressor and an air conditioner provided according to some embodiments of the present invention.

[0065] Combined with Figure 1 、 Figure 2 、 Figure 3 And Figure 4As shown, in some embodiments of the present invention, a compressor 100 is provided. The compressor 100 includes: a bearing 110, a rotating shaft 160, a muffler 120, and a rotor 130. The bearing 110 includes a main body portion 111 and a supporting portion 112. The supporting portion 112 is provided on the main body portion 111, and a first exhaust hole 113 is provided on the main body portion 111. The rotating shaft 160 is connected to the bearing 110. The muffler 120 is connected to the main body portion 111. An installation hole 121 and a second exhaust hole 122 are provided on the muffler 120. The rotating shaft 160 passes through the installation hole 121. The second exhaust hole 122 is communicated with the first exhaust hole 113. The second exhaust hole 122 is provided on the side of the muffler 120, and the opening direction of the second exhaust hole 122 faces away from the main body portion 111. The rotor 130 is located on the side of the muffler 120 away from the main body portion 111, and the rotor 130 is sleeved on the rotating shaft 160.

[0066] The bearing 110 includes a main body portion 111 and a supporting portion 112. A first exhaust hole 113 is formed on the main body portion 111 by machining. The supporting portion 112 is arranged at the central position of the main body portion 111, and the supporting portion 112 extends along the axial direction of the compressor 100. The muffler 120 is fixed on the main body portion 111. The gas discharged from the first exhaust hole 113 can flow into the muffler 120, and the muffler 120 performs noise reduction treatment on the airflow discharged from the first exhaust hole 113. The rotor 130 is arranged on the side of the muffler 120 away from the main body portion 111. The rotating shaft 160 is connected to the bearing 110, and the bearing 110 supports the rotating shaft 160. The rotating shaft 160 passes through the installation hole 121, and a part of the rotating shaft 160 passing through the installation hole 121 is connected to the rotor 130. The rotor 130 is sleeved on the rotating shaft 160.

[0067] A second exhaust hole 122 is formed on the muffler 120 by machining. The gas flowing into the muffler 120 can be discharged outward through the second exhaust hole 122. If the second exhaust hole 122 is provided on the side of the muffler 120 facing the rotor 130, during the exhaust process, the exhaust will impact the rotating rotor 130, forming airflow cutting near the rotor 130, which will increase the exhaust pulsation, affect the exhaust noise, and deteriorate the total noise value and sound quality of the compressor 100. If the second exhaust hole 122 is provided on the side of the muffler 120, and the opening direction of the second exhaust hole 122 is along the radial direction of the compressor 100, at this time, the exhaust mode is radial exhaust, that is, the exhaust is directed at the inner wall surface of the housing of the compressor 100. In this exhaust mode, the gas will impact the inner wall surface of the housing, generating a large-scale refrigerant gas circulation. The gas circulation will impact the surface of the oil sump, resulting in poor oil return effect and deteriorating the risk of the oil level surface of the compressor 100.

[0068] In this solution, the second exhaust hole 122 is arranged on the side of the muffler 120, which is equivalent to increasing the distance between the second exhaust hole 122 and the rotor 130. The gas flowing out of the second exhaust hole 122 gradually diffuses, and the gas discharged from the second exhaust hole 122 is not likely to flow towards the rotor 130, or only a small amount of gas flows towards the rotor 130. Therefore, the gas discharged from the second exhaust hole 122 is not likely to impact the rotating rotor 130, so it is not easy to form air flow cutting near the rotor 130, reducing the exhaust pulsation, and further reducing the exhaust noise, optimizing the total noise value and sound quality of the compressor 100.

[0069] The opening direction of the second exhaust hole 122 in this solution ( Figure 4 the arrow direction at A) deviates from the main body part 111. At this time, the exhaust mode is not radial exhaust, and the gas discharged from the second exhaust hole 122 does not directly flow towards the inner wall surface of the housing of the compressor 100. In this exhaust mode, the gas is not likely to impact the inner wall surface of the housing, and the gas is not likely to impact the surface of the oil sump, improving the oil return effect.

[0070] It can be seen that in this solution, the setting method of the second exhaust hole 122, on the basis of optimizing the oil return effect, the muffler 120 can also effectively reduce the impact noise of the exhaust refrigerant on the rotor, realizing the functions of vibration reduction and noise reduction.

[0071] This embodiment provides a side exhaust silencing structure. The second exhaust hole 122 is arranged on the side wall surface of the muffler 120. The specific exhaust guide structure enables the air flow to flow upward without impacting the inner wall surface of the housing of the compressor 100, nor directly impacting the rotating rotor 130, and can make better use of the volume of the lower cavity of the motor. The muffler 120 structure of this invention has a higher sound absorption amount, better reduces the exhaust pulsation noise, and at the same time, the exhaust air flow will not form an impact on the motor rotor 130 during the exhaust process, effectively avoiding the rotating rotor 130 from cutting the exhaust air flow, reducing the force on the rotor 130, not only effectively reducing the exhaust pulsation noise, but also avoiding the large-scale circulation generated by the traditional side exhaust muffler impacting the wall surface during the exhaust process, avoiding impacting the oil liquid surface, and having a better oil return effect.

[0072] Technical advantages: Using the structure of this invention, the sound absorption effect is the best in the medium and low frequency range within 2000 Hz and the high frequency range above 3500 Hz in the transmission loss simulation. The actual test shows that the noise peak value in the frequency range of 500 Hz to 2000 Hz is reduced by more than 3 dB, and the noise reduction effect is remarkable. The simulation of the oil level of the compressor 100 shows that the side exhaust axial exhaust and the side exhaust radial exhaust have basically the same sound absorption amount, but it improves the large-scale circulation generated by the radial side exhaust impacting the wall surface, avoids impacting the surface of the oil sump, has a better oil return effect, and improves the reliability.

[0073] Combined with Figure 1 、 Figure 2 、 Figure 3 and Figure 4As shown, in some embodiments, optionally, the silencer 120 includes: a silencer body 123 and a flow guiding portion 124. An opening 125 is provided on the side wall of the silencer body 123. The flow guiding portion 124 is connected to the side wall of the silencer body 123. A second exhaust hole 122 is formed between the flow guiding portion 124 and the silencer body 123, and the second exhaust hole 122 communicates with the opening 125.

[0074] An opening 125 is machined on the side wall of the silencer body 123. The opening direction of the opening 125 faces the housing of the compressor 100. In order to prevent the gas from impacting the inner wall surface of the housing of the compressor 100, a flow guiding portion 124 is provided outside the silencer body 123. A second exhaust hole 122 is formed between the flow guiding portion 124 and the side wall of the silencer body 123. By providing the flow guiding portion 124, the flow direction of the gas flowing out of the opening 125 can be changed, so that the gas is not likely to flow towards the inner wall surface of the housing.

[0075] By providing the flow guiding portion 124 on the silencer body 123 for guiding the flow, it is not necessary to make excessive modifications to the shape of the silencer body 123, thereby reducing the processing difficulty of the silencer 120.

[0076] In a possible application, the flow guiding portion 124 and the silencer body 123 are of an integral structure, or the flow guiding portion 124 is fixed to the silencer body 123 by welding.

[0077] Combined with Figure 1 、 Figure 2 、 Figure 3 and Figure 4 As shown, in some embodiments, optionally, the side portion of the flow guiding portion 124 is parallel to the side wall of the silencer body 123, or there is an included angle between the side portion of the flow guiding portion 124 and the side wall of the silencer body 123.

[0078] The side portion of the flow guiding portion 124 can be set parallel to the side wall of the silencer body 123. In this case, the side portion of the flow guiding portion 124 extends along the axial direction of the compressor 100, and the opening 125 direction of the second exhaust hole 122 is parallel to the axial direction of the compressor 100. The gas discharged from the second exhaust hole 122 flows along the axial direction of the compressor 100. At this time, the gas discharged from the second exhaust hole 122 is not likely to impact the inner wall surface of the housing.

[0079] Alternatively, an included angle can also be provided between the side portion of the flow guiding portion 124 and the side wall of the silencer body 123. The airflow flowing out of the second exhaust hole 122 flows obliquely with respect to the axial direction of the compressor 100. In this case, the gas discharged from the second exhaust hole 122 is not likely to impact the inner wall surface of the housing, and moreover, the obliquely flowing airflow is not likely to impact the rotor 130, further reducing the exhaust pulsation, and thus further reducing the exhaust noise.

[0080] Combined Figure 1 、 Figure 2 、 Figure 3 and Figure 4 As shown, in some embodiments, optionally, there is an included angle α1 between the side portion of the flow deflector 124 and the side wall of the muffler body 123, and the included angle α1 satisfies the following range: 5° < α1 < 80°.

[0081] There is an included angle between the side portion of the flow deflector 124 and the side wall of the muffler body 123. If the included angle between the side portion of the flow deflector 124 and the side wall of the muffler body 123 is too small, a large amount of air flow directly flows towards the rotor 130, which may impact the rotor 130. If the included angle between the side portion of the flow deflector 124 and the side wall of the muffler body 123 is too large, the air flow discharged from the second exhaust hole 122 may impact the inner wall surface of the housing of the compressor 100. To avoid the above situations, in this solution, it is defined that the included angle α1 between the side portion of the flow deflector 124 and the side wall of the muffler body 123 satisfies the following condition: 5° < α1 < 80°. Within this range, the air flow discharged from the second exhaust hole 122 is not likely to impact the rotor 130 and the inner wall surface of the housing. On the basis of optimizing the oil return effect, the muffler 120 can also effectively reduce the dynamic noise of the refrigerant gas.

[0082] Exemplarily, α1 is 6°, 50°, or 79°.

[0083] Combined Figure 1 、 Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 、 Figure 7 、 Figure 8 and Figure 9 As shown, in some embodiments, optionally, the muffler body 123 includes a plurality of convex portions 126 and a plurality of concave portions 127. In the circumferential direction of the muffler body 123 ( Figure 5 the arrow direction at C in

[0084] ), a concave portion 127 is provided between two adjacent convex portions 126, and a convex portion 126 is provided between two adjacent concave portions 127. The number of the flow deflectors 124 is at least one, and the flow deflectors 124 are provided on the convex portions 126 and / or the concave portions 127.A plurality of convex portions 126 and a plurality of concave portions 127 are provided in the circumferential direction of the muffler body 123, and the plurality of convex portions 126 and the plurality of concave portions 127 are arranged at intervals in turn. When a concave portion 127 is provided between two convex portions 126, a connection hole can be provided between the two convex portions 126, and a connection member is used to pass through the connection hole, so as to lock the muffler 120 on the bearing 110. In this case, the distance from the connection hole to the center of the muffler 120 is small. If the concave portion 127 is not provided on the muffler body 123, the connection hole needs to be provided on the side of the convex portion 126 away from the center line, resulting in an oversize muffler 120.

[0085] A flow guiding portion 124 can be provided on at least one of the convex portion 126 and the concave portion 127. The setting position of the flow guiding portion 124 is relatively flexible. Whether the flow guiding portion 124 is provided on the convex portion 126 or the concave portion 127, an effective noise reduction effect can be achieved. The position of the flow guiding portion 124 can be set accordingly according to the layout of the muffler 120 and surrounding components, which is beneficial to improving the rationality of the internal layout of the compressor 100.

[0086] Figure 9 In it, flow guiding portions 124 are respectively provided on two non-adjacent convex portions 126, Figure 9 In it, the two dashed-line areas are two flow guiding portions 124.

[0087] Combined with Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 and Figure 6 As shown in, in some embodiments, optionally, rivet holes 114 are provided on the main body portion 111, and the compressor 100 further includes a valve plate 140 and rivets 150 ( Figure 2 In it, the valve plate 140 and the rivets 150 are exemplary structures, and the shapes of the valve plate 140 and the rivets 150 are not limited to Figure 2 the shapes in it), the rivets 150 are connected to the rivet holes 114, and the rivets 150 are used to lock the valve plate 140 on the main body portion 111.

[0088] The plurality of convex portions 126 include a first convex portion 1261 and a second convex portion 1262, and the plurality of concave portions 127 include a first concave portion 1271 and a second concave portion 1272. Along the axial direction of the compressor 100 ( Figure 3 the arrow direction at D in it), the first convex portion 1261 faces the first exhaust hole 113, the second convex portion 1262 faces the rivet hole 114, the first concave portion 1271 is located between the first convex portion 1261 and the second convex portion 1262, and the second concave portion 1272 is located on the side of the second convex portion 1262 away from the first concave portion 1271. A flow guiding portion 124 is provided on at least one of the first convex portion 1261, the second convex portion 1262, the first concave portion 1271, and the second concave portion 1272.

[0089] There are multiple protrusions 126, and two of the multiple protrusions 126 are respectively a first protrusion 1261 and a second protrusion 1262. There are also multiple concave portions 127, and two of the multiple concave portions 127 are respectively a first concave portion 1271 and a second concave portion 1272. The first protrusion 1261, the first concave portion 1271, the second protrusion 1262, and the second concave portion 1272 are sequentially arranged in the circumferential direction of the muffler body 123.

[0090] A rivet hole 114 is provided on the main body 111 , and the rivet 150 passes through the rivet hole 114 , so as to lock the valve plate 140 on the main body 111 . The valve plate 140 is used to open or close the first exhaust hole 113 .

[0091] Along the axial direction of the compressor 100, the first protrusion 1261 faces the first exhaust hole 113, the second protrusion 1262 faces the rivet hole 114, the first protrusion 1261, the first recess 1271, the second protrusion 1262 and the second recess 1272 face the exhaust area on the main body 111. When the guide portion 124 is set on any one of the first protrusion 1261, the first recess 1271, the second protrusion 1262 and the second recess 1272, the mid- and low-frequency noise can be effectively reduced, which is beneficial to controlling the mid- and low-frequency noise levels.

[0092] Combination Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 and Figure 6 As shown, in some embodiments, optionally, the line connecting the center line of the bearing 110 and the center line of the first exhaust hole 113 is L1, and the line L1 is along the radial direction of the bearing 110 ( Figure 3 The arrow at R in the figure points to the direction of extension.

[0093] When the air guide portion 124 is disposed on the first convex portion 1261 or the first concave portion 1271 , a line L2 is formed between the center line of the bearing 110 and the center line of the second exhaust hole 122 , and the line L2 extends along the radial direction of the bearing 110 .

[0094] When the guide portion 124 is disposed on the side of the line L1 away from the second protrusion 1262, the angle between the lines L1 and L2 is α2, and α2 is less than 40°. When the guide portion 124 is disposed on the side of the line L1 adjacent to the second protrusion 1262 or on the first recess 1271, the angle between the lines L1 and L2 is α3, and α3 is less than 45°.

[0095] If the guide portion 124 is disposed on the first convex portion 1261 or the first concave portion 1271 , in order to improve the noise control effect, it is necessary to limit the disposition range of the guide portion 124 on the first convex portion 1261 or the first concave portion 1271 .

[0096] The line connecting the center line of the bearing 110 and the center line of the first exhaust hole 113 is L1 , and the line connecting the center line of the bearing 110 and the center line of the second exhaust hole 122 is L2 . Both the line L1 and the line L2 extend in the radial direction of the bearing 110 .

[0097] The direction from the first convex portion 1261 to the second convex portion 1262 is set to be the clockwise direction. In the clockwise direction, with the line L1 as the reference, the angle between the line L2 and the line L1 is greater than -40° and less than 45°. That is, when the air guide 124 is arranged on the side of the line L1 away from the second convex portion 1262, the angle between the line L1 and the line L2 is less than 40°. When the air guide 124 is arranged on the side of the line L1 adjacent to the second convex portion 1262 or arranged on the first concave portion 1271, the angle between the lines L1 and L2 is less than 45°. In the case of this range, the noise of the exhaust gas at the medium and low frequencies can be effectively reduced, which is conducive to controlling the level of the medium and low frequency noise.

[0098] Combination Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 and Figure 6 As shown, in some embodiments, optionally, a line connecting the center line of the bearing 110 and the center line of the first exhaust hole 113 is L1, and the line L1 extends along the radial direction of the bearing 110.

[0099] When the guide portion 124 is disposed on the second protrusion 1262 or the second recess 1272, the line connecting the center line of the bearing 110 and the center line of the second exhaust hole 122 is L3, and the line L3 extends along the radial direction of the bearing 110. The angle between the line L1 and the line L3 is α4, and 10°<α4<140°.

[0100] If the guide portion 124 is disposed on the second convex portion 1262 or the second concave portion 1272 , in order to improve the noise control effect, it is necessary to limit the setting range of the guide portion 124 on the second convex portion 1262 or the second concave portion 1272 .

[0101] A line connecting the center line of the bearing 110 and the center line of the first exhaust hole 113 is L1 , and a line connecting the center line of the bearing 110 and the center line of the second exhaust hole 122 is L3 .

[0102] Set the direction from the first convex part 1261 to the second convex part 1262 as the clockwise direction. Connecting line L1 and connecting line L2 are arranged in sequence along the clockwise direction. There is an included angle α4 between connecting line L1 and connecting line L2, where 10° < α4 < 140°. In this range, the noise of the exhaust gas in the medium and low frequencies can be effectively reduced, which is beneficial to controlling the medium and low frequency noise level.

[0103] Combined with Figure 1 、 Figure 2 、 Figure 3 and Figure 4 As shown in, in some embodiments, optionally, the rotor 130 and the guide part 124 are projected on the main body part 111, and the projection of the rotor 130 and the projection of the guide part 124 are spaced apart from each other.

[0104] The projections of the rotor 130 and the guide part 124 on the main body part 111 are spaced apart from each other, and the projection of the second exhaust hole 122 is located outside the projection of the rotor 130. Therefore, along the axial direction of the compressor 100, the guide part 124 and the rotor 130 are misaligned. So, the second exhaust hole 122 and the rotor 130 are also misaligned. Even if the opening direction of the second exhaust hole 122 is parallel to the axial direction of the compressor 100, the air flow flowing out of the second exhaust hole 122 is not likely to directly flow towards the rotor 130, which can further reduce the impact of the air flow on the rotating shaft, thereby further reducing the exhaust pulsation noise.

[0105] In some embodiments, optionally, when the number of the second exhaust holes 122 is one, the opening area of the second exhaust hole 122 is S1, and the opening area of the first exhaust hole 113 is S2, where 0.4 < S1 / S2 < 1.5. When the number of the second exhaust holes 122 is multiple, the sum of the opening areas of the multiple second exhaust holes 122 is S1, and the opening area of the first exhaust hole 113 is S2, where 0.4 < S1 / S2 < 1.5.

[0106] The number of the guide parts 124 can be one or multiple. Therefore, the number of the second exhaust holes 122 can also be one or multiple. When the number of the second exhaust holes 122 is one, the following condition is satisfied between the opening area S1 of the second exhaust hole 122 and the opening area S2 of the first exhaust hole 113: 0.4 < S1 / S2 < 1.5. In this range, the exhaust gas can be smoothly discharged from the second exhaust hole 122. Moreover, within the above range, the noise during the exhaust process can be reduced, which is beneficial to controlling the medium and low frequency noise level.

[0107] When the number of the second exhaust holes 122 is multiple, the sum of the opening areas of the multiple second exhaust holes 122 is S1, and the following condition is satisfied between S1 and the opening area S2 of the first exhaust hole 113: 0.4 < S1 / S2 < 1.5. Within this range, it is also possible to ensure smooth exhaust from the second exhaust holes 122 and reduce the noise during the exhaust process.

[0108] Combined with Figure 1 , Figure 2 , Figure 3 and Figure 4 shown, in some embodiments, optionally, the first side of the silencer 120 faces the rotor 130, and the second exhaust holes 122 are spaced from the first side of the silencer body 123.

[0109] The first side of the silencer 120 is adjacent to the rotor 130. Spacing the second exhaust holes 122 from the first side of the silencer body 123 can further move the second exhaust holes 122 away from the rotor 130, thereby further reducing the impact of the exhaust on the rotor 130, further reducing the exhaust pulsation, and further reducing the exhaust noise.

[0110] Combined with Figure 1 , Figure 2 , Figure 3 and Figure 4 shown, in some embodiments, optionally, the second side of the silencer 120 faces the main body portion 111. Along the axial direction of the compressor 100, the distance between the first exhaust hole 113 and the second side of the silencer 120 is H1, and the axial length of the silencer 120 is H2. The following condition is satisfied between H1 and H2: 0.2 < H1 / H2 < 0.8.

[0111] The distance between the first exhaust hole 113 and the second side of the silencer 120 is H1, and the overall axial length of the silencer 120 is H2. When the ratio of H1 to H2 is too large, the second exhaust holes 122 are too close to the first side of the silencer 120, and there is a risk of the exhaust gas flow impacting the rotor 130. When the ratio of H1 to H2 is too small, the second exhaust holes 122 are too far from the first side of the silencer 120. At this time, the setting position of the flow guiding portion 124 is limited, resulting in greater processing difficulty for the silencer 120.

[0112] In this solution, it is defined that H1 and H2 satisfy the following condition: 0.2 < H1 / H2 < 0.8. Within this range, there is sufficient spacing between the second exhaust holes 122 and the rotor 130 to avoid the exhaust gas flow impacting the rotor 130, and the second exhaust holes 122 are not too far from the first side of the silencer 120, thereby leaving sufficient space for the setting position of the flow guiding portion 124 and facilitating the processing of the silencer 120.

[0113] In an embodiment of the present invention, an exhaust system and a rotary compressor 100 are provided, including a bearing 110 and a muffler 120 disposed in a sealed housing. The muffler 120 is placed on the bearing 110. The number of petals n of the muffler 120 is n≥2. A second exhaust hole 122 and an exhaust flow guiding structure are provided on the side wall surface of the muffler 120 for discharging the compressed refrigerant gas outside the muffler 120.

[0114] The exhaust direction of the second exhaust hole 122 on the side wall surface of the muffler 120 is upward or obliquely upward. In the cross-sectional view of the exhaust flow guiding structure of the muffler 120 ( Figure 4 ), the included angle between the maximum inclined line and the side wall surface of the muffler 120 where it is located is α1, satisfying 5° < α1 < 80°, which is beneficial to guiding the exhaust air flow.

[0115] During the operation of the compressor 100, the second exhaust hole 122 and the flow guiding structure are away from the rotating rotor 130 and the balance weight. On the one hand, in the height direction, the second exhaust hole 122 and the flow guiding structure are relatively far from the lower surface of the rotor 130 and the lower balance weight. On the other hand, in the horizontal direction, different from the position of the exhaust hole of the traditional muffler 120 within the outer circle projection of the rotor 130, in the structure of the present invention, the second exhaust hole 122 is located outside the outer circle projection of the rotor 130. The muffler 120 structure of this invention has a higher sound absorption capacity, better reduces the exhaust pulsation noise, and at the same time does not cause the exhaust air flow to impact the rotor 130 during the exhaust process, effectively avoiding the rotating rotor 130 from cutting the exhaust air flow, reducing the force on the rotor 130, reducing the exhaust pulsation noise, and reducing the wind friction power consumption of the rotor 130.

[0116] As Figure 9 shown, the muffler 120 has convex portions 126 similar to 5 petals. The convex portions 126 where each petal of the muffler 120 is located are numbered for facilitating the description of the scheme design. Relative to the structure of the bearing 110, the convex portion 126 corresponding to above the first exhaust hole 113 of the bearing 110 is defined as petal 1. Then rotate clockwise, and the convex portion 126 corresponding to above the rivet hole 114 of the bearing 110 is defined as petal 2. Rotate clockwise in sequence, and the remaining three convex portions 126 are respectively defined as petal 3, petal 4, and petal 5.

[0117] Figure 10The sound attenuation effect on noises of different frequencies when the second exhaust hole 122 is arranged at different convex parts 126 is shown. When the position of the second exhaust hole 122 of the muffler 120 is arranged on the side wall surface of 1 lobe corresponding to the upper part of the first exhaust hole 113, or on the side wall surface of 2 lobes corresponding to the upper part of the rivet hole 114, the sound attenuation amount in the medium and low frequency range within 2000 Hz is the highest, which is beneficial to controlling the medium and low frequency noise level. Further, taking the top view of the plane where the inner diameter center line of the bearing 110 and the center line of the first exhaust hole 113 are located together as the reference line, the included angle α4 between the center line of the second exhaust hole 122 on the side wall surface of 2 lobes corresponding to the upper part of the rivet hole 114 and the plane of the inner diameter center line of the bearing 110 and the above-defined reference line is defined, and 10° < α4 < 140°. The corresponding sound attenuation effect of the muffler 120 is as Figure 10 shown. The sound attenuation amount in the medium and low frequency range within 2000 Hz and the high frequency range above 3500 Hz is the highest, and the sound attenuation amounts in other frequency ranges are quite equivalent, and the overall sound attenuation effect is optimal.

[0118] The height of the muffler 120 is H2, and the height from the second exhaust hole 122 to the lower surface of the muffler 120 is H1, and 0.2 < H1 / H2 < 0.8. The structure of this invention has a better sound attenuation effect on medium and low frequency and high frequency exhaust noises. During the exhaust process, the exhaust air flow will not form an impact on the rotor 130, effectively avoiding the rotating rotor 130 from cutting the exhaust air flow, reducing the force on the rotor 130, effectively reducing the exhaust pulsation noise, and avoiding the large-scale circulation generated by the traditional side exhaust muffler 120 hitting the wall surface during the exhaust process, avoiding hitting the oil liquid surface, and having a better oil return effect.

[0119] Combined with Figure 11 、 Figure 12 and Figure 13 shown, adopting the technical solution of this invention, the noise peaks in the frequency range of 500 Hz to 2000 Hz are generally reduced by 3 dB to 8.5 dB, and the auditory perception of the medium and low frequency noises of the compressor 100 and the air conditioning system is significantly improved. In addition, compared with the annular exhaust mode of the traditional muffler 120, for the axial side wall surface exhaust mode of this invention, the axial gas force on the rotor 130 can be reduced by 70.5%, which is equivalent to that of the radial side exhaust muffler 120. However, compared with the traditional radial side exhaust muffler 120, the technical solution of this invention can increase the oil storage amount in the lower cavity oil pool of the compressor 100 by 55.8%, ensure the oil supply and lubrication on the upper part of the compressor 100, significantly improve the reliability of the compressor 100, and avoid the wear of parts.

[0120] One or more second exhaust holes 122 can be arranged at different convex parts 126 or different concave parts 127 of the exhaust hole, or one or more second exhaust holes 122 can also be arranged at the same convex part 126 or concave part 127.

[0121] The compressor in this embodiment can be a single-cylinder, double-cylinder or multi-cylinder compressor.

[0122] In an embodiment of the present invention, an air conditioner is provided, which includes the compressor in any of the above embodiments, and the air conditioner can achieve the technical effects in any of the above embodiments, which will not be elaborated herein again.

[0123] In the present invention, the term "a plurality of" refers to two or more, unless otherwise clearly defined. Terms such as "installed", "connected", "coupled", "fixed", etc. should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; "coupled" can be a direct connection or an indirect connection through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0124] In the description of this specification, the descriptions of terms such as "an embodiment", "some embodiments", "specific embodiments", etc. mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or instance. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0125] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, various modifications and changes can be made to the present invention. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A compressor, characterized in that, Comprising: A bearing, the bearing including a main body portion and a support portion, the support portion being provided on the main body portion, and a first exhaust hole being provided on the main body portion; A rotating shaft connected to the bearing; A silencer connected to the main body portion, the silencer being provided with a mounting hole and a second exhaust hole, the rotating shaft passing through the mounting hole, the second exhaust hole communicating with the first exhaust hole, the second exhaust hole being provided on a side portion of the silencer, and an opening direction of the second exhaust hole facing away from the main body portion; A rotor located on a side of the silencer away from the main body portion, the rotor being sleeved on the rotating shaft.

2. The compressor according to claim 1, characterized in that, The silencer includes: A silencer body, an opening being provided on a side wall of the silencer body; A diversion portion connected to the side wall of the silencer body, a second exhaust hole being formed between the diversion portion and the silencer body, the second exhaust hole communicating with the opening.

3. The compressor according to claim 2, characterized in that, A side portion of the diversion portion is parallel to the side wall of the silencer body, or an included angle exists between the side portion of the diversion portion and the side wall of the silencer body.

4. The compressor according to claim 2, characterized in that, An included angle α1 exists between the side portion of the diversion portion and the side wall of the silencer body, and the included angle α1 satisfies the following range: 5° < α1 < 80°.

5. The compressor according to any one of claims 2 to 4, characterized in that, The silencer body includes a plurality of convex portions and a plurality of concave portions. In a circumferential direction of the silencer body, a concave portion is provided between two adjacent convex portions, and a convex portion is provided between two adjacent concave portions. The number of the diversion portions is at least one, and the diversion portion is provided on the convex portion and / or the concave portion.

6. The compressor according to claim 5, characterized in that, A rivet hole is provided on the main body portion, and the compressor further includes a valve plate and a rivet. The rivet is connected to the rivet hole, and the rivet is used to lock the valve plate on the main body portion; The plurality of convex portions include a first convex portion and a second convex portion, and the plurality of concave portions include a first concave portion and a second concave portion. Along an axial direction of the compressor, the first convex portion faces the first exhaust hole, the second convex portion faces the rivet hole, the first concave portion is located between the first convex portion and the second convex portion, and the second concave portion is located on a side of the second convex portion away from the first concave portion; Wherein, the diversion portion is provided on at least one of the first convex portion, the second convex portion, the first concave portion, and the second concave portion.

7. The compressor according to claim 6, characterized in that, A connecting line between a center line of the bearing and a center line of the first exhaust hole is L1, and the connecting line L1 extends along a radial direction of the bearing; When the diversion portion is provided on the first convex portion or the first concave portion, a connecting line between a center line of the bearing and a center line of the second exhaust hole is L2, and the connecting line L2 extends along a radial direction of the bearing; When the diversion portion is provided on a side of the connecting line L1 away from the second convex portion, an included angle between the connecting line L1 and the connecting line L2 is α2, and α2 < 40°. When the diversion portion is provided on a side of the connecting line L1 adjacent to the second convex portion or on the first concave portion, an included angle between the connecting line L1 and the connecting line L2 is α3, and α3 < 45°.

8. The compressor according to claim 6, wherein A connecting line between a center line of the bearing and a center line of the first exhaust hole is L1, and the connecting line L1 extends along a radial direction of the bearing; When the diversion part is arranged on the second convex part or the second concave part, the connecting line between the center line of the bearing and the center line of the second exhaust hole is L3, the connecting line L3 extends along the radial direction of the bearing, and the included angle between the connecting line L1 and the connecting line L3 is α4, 10° < α4 < 140°.

9. The compressor according to any one of claims 2 to 4, characterized in that, The rotor and the diversion part are projected on the main body part, and the projection of the rotor is spaced from the projection of the diversion part.

10. The compressor according to any one of claims 1 to 4, characterized in that When the number of the second exhaust holes is one, the opening area of the second exhaust hole is S1, the opening area of the first exhaust hole is S2, 0.4 < S1 / S2 < 1.5; When the number of the second exhaust holes is multiple, the sum of the opening areas of the multiple second exhaust holes is S1, the opening area of the first exhaust hole is S2, 0.4 < S1 / S2 < 1.

5.

11. The compressor according to any one of claims 2 to 4, characterized in that, The first side of the silencer faces the rotor, and the second exhaust hole is arranged at an interval from the first side of the silencer body.

12. The compressor according to any one of claims 1 to 4, characterized in that, The second side of the silencer faces the main body part. Along the axial direction of the compressor, the distance between the first exhaust hole and the second side of the silencer is H1, and the axial length of the silencer is H2. H1 and H2 satisfy the following condition: 0.2 < H1 / H2 < 0.

8.

13. An air conditioner, characterized in that, Comprising: The compressor according to any one of claims 1 to 12.

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