Compressor and air conditioning unit
By introducing liquid noise reduction fluid into the compressor of the air-conditioning unit, and using high-speed exhaust atomization to form a mist fluid, absorbing high-frequency noise caused by high-speed exhaust friction, the problem of high-frequency noise is solved and effective The noise is reduced.
Patent Information
- Application Number
- CN202411866885.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-18
- Publication Date
- 2025-02-14
Smart Images
Figure CN119435461A_ABST
Abstract
Description
Technical Field
[0001] The present application relates to the technical field of compression equipment, and in particular to a compressor and an air-conditioning unit. Background Art
[0002] Air conditioning units, especially central air conditioning units, are noisy during operation. The noise of air conditioning units is mainly caused by the refrigeration compressor. When the compressor is working, the refrigerant gas is sucked in from the suction pipe and enters the rotating impeller through the impeller inlet. Due to the high-speed rotation of the impeller, the blades push the refrigerant gas along the flow channel of the impeller from the center to the radial outer end. Finally, when the gas flows out from the impeller outlet at the radial outer end of the impeller, the pressure and absolute speed of the refrigerant gas are increased, forming high-speed exhaust. Noise is generated when the high-speed exhaust flows into the diffuser, and the noise there is the main source of compressor noise.
[0003] The above statements are only used to provide background information related to the present application and do not necessarily constitute prior art. Summary of the invention
[0004] The purpose of the present application is to provide a compressor and an air-conditioning unit, aiming to reduce the operating noise of the compressor and the air-conditioning unit.
[0005] The first aspect of the present application provides a compressor, comprising: a rotating shaft; an impeller connected to the rotating shaft, having an impeller inlet located at an axial first end of the impeller and an impeller outlet located at a radial outer end of the impeller; a diffuser located radially outside the impeller, having a diffuser flow channel and a diffuser inlet, a diffuser outlet and a noise reduction fluid inlet connected to the diffuser flow channel, the diffuser inlet being opposite to the impeller outlet, and the noise reduction fluid inlet being configured to transport liquid noise reduction fluid into the diffuser flow.
[0006] In the compressor of some embodiments, the noise reduction fluid inlet is configured to deliver the noise reduction fluid to the diffuser inlet of the diffuser flow passage.
[0007] In some embodiments of the compressor, the diffuser includes an end wall located along the axial direction of the impeller at one end away from the impeller inlet, and the noise reduction fluid inlet is arranged on the end wall; the compressor also includes an oil-blocking sleeve, which is located at the second axial end of the impeller and has a gap with the end surface of the second axial end of the impeller, and the gap is connected to the noise reduction fluid inlet, and the noise reduction fluid inlet receives the noise reduction fluid through the gap.
[0008] In the compressor of some embodiments, the oil-blocking sleeve is integrally provided with the end wall; and / or the noise reduction fluid inlet is an annular opening coaxial with the impeller.
[0009] In the compressor of some embodiments, the shaft has a hollow portion, a shaft inlet for conveying the noise reduction fluid to the hollow portion, a shaft outlet for outputting the noise reduction fluid from the hollow portion, and a connecting hole connecting the hollow portion and the shaft outlet, and the shaft outlet is connected to the gap.
[0010] In some embodiments of the compressor, the hollow portion includes a center hole arranged in the radial middle of the rotating shaft, wherein the diameter of the center hole is 1 / 8 to 1 / 10 of the maximum diameter of the rotating shaft; and / or a turbulent structure is provided on the hole wall of the center hole.
[0011] In the compressor of some embodiments, the hollow portion includes a constricted section provided at the shaft inlet, and the flow area of the constricted section gradually decreases from the shaft inlet to a side away from the shaft inlet.
[0012] In some embodiments of the compressor, the shaft includes two or more shaft outlets arranged along the circumference of the shaft and two or more connecting holes corresponding one by one to the two or more shaft outlets; and / or along the axial direction of the impeller, the shaft outlet is opposite to the radial inner side of the interval.
[0013] In some embodiments of the compressor, the two or more rotating shaft outlets and the two or more connecting holes are evenly arranged along the circumference of the rotating shaft; and / or the number of the two or more rotating shaft outlets and the two or more connecting holes is greater than or equal to the number of blades of the impeller; and / or the sum of the flow areas of the two or more rotating shaft outlets is equal to the sum of the flow areas of the center hole, and / or the sum of the flow areas of the two or more connecting holes is equal to the sum of the flow areas of the center hole.
[0014] In the compressor of some embodiments, the communicating hole is inclined from the hollow portion to the shaft outlet along a direction from the axial second end to the axial first end of the shaft.
[0015] In the compressor of some embodiments, the angle between the connecting hole and the axis of the rotating shaft is greater than or equal to 80° and less than 90°.
[0016] In some embodiments of the compressor, the impeller is arranged at the first axial end of the rotating shaft, and the rotating shaft inlet is arranged on the end surface of the second axial end of the rotating shaft; the compressor also includes an end cover, which is rotatable relative to the rotating shaft and is arranged at the rotating shaft inlet, and the end cover is provided with a port connected to the rotating shaft inlet, and a sealing structure is provided between the end cover and the rotating shaft.
[0017] In some embodiments of the compressor, the end cover includes an end wall and a side wall connected to the outer periphery of the end wall, the port is arranged on the end wall, the side wall is sleeved on the axial second end of the rotating shaft, and the sealing structure is arranged on the side wall.
[0018] In the compressor of some embodiments, a buffer chamber communicating with the port and the inlet of the rotating shaft is formed between the end cover and the rotating shaft.
[0019] The second aspect of the present application provides an air-conditioning unit, which includes a compressor, a condenser, a throttling device and an evaporator connected as a refrigerant circuit through a refrigerant pipeline; the compressor is the compressor described in the first aspect; the air-conditioning unit also includes a conduit, and the noise reduction fluid inlet receives the liquid refrigerant in the condenser as the noise reduction fluid through the conduit.
[0020] Based on the compressor provided in the present application, after the liquid noise reduction fluid enters the diffuser flow channel through the noise reduction fluid inlet, it is atomized to form a mist fluid under the action of high-speed exhaust gas. The tiny droplets carried by the mist fluid can absorb the sound energy of the high-frequency noise caused by the friction of the high-speed exhaust gas, thereby achieving the purpose of reducing the operating noise of the compressor.
[0021] The air conditioning unit of the embodiment of the present application has the advantages of the compressor of the embodiment of the present application.
[0022] Other features and advantages of the present application will become apparent from the following detailed description of exemplary embodiments of the present application with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS
[0023] The drawings described herein are used to provide a further understanding of the present application and constitute a part of the present application. The illustrative embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:
[0024] Figure 1 This is a schematic diagram of the principles of an air-conditioning unit according to some embodiments of the present application.
[0025] Figure 2 This is a schematic diagram of the principle cross-sectional structure of a compressor according to some embodiments of the present application.
[0026] Figure 3 This is a schematic structural diagram of the combined structure of the rotating shaft, end cover and conduit of the compressor in some embodiments of the present application.
[0027] Figure 4 for Figure 3 A schematic structural diagram of the connecting pipe of the combined structure shown.
[0028] Figure 5 for Figure 3A schematic structural diagram of the end cover of the combined structure shown.
[0029] Figures 1 to 5 In the figure, each reference numeral represents:
[0030] 1. Compressor;
[0031] 2. Condenser;
[0032] 3. Throttling device;
[0033] 4. Evaporator;
[0034] 5. Refrigerant pipeline;
[0035] 9. Catheter;
[0036] 10. rotating shaft; 11. hollow portion; 111. constricted section; 12. rotating shaft inlet; 13. rotating shaft outlet; 14. connecting pipe;
[0037] 20. Impeller; 21. Blades; 22. Impeller inlet; 23. Impeller outlet;
[0038] 30. Diffuser; 31. End wall; 32. Diffuser inlet; 33. Pressure protector outlet; 34. Diffuser flow channel; 35. Noise reduction fluid inlet;
[0039] 40. Oil blocking sleeve;
[0040] 50. Interval;
[0041] 60. End cover; 61. End wall; 62. Side wall; 63. Port; 64. Sealing structure; C. Buffer chamber. DETAILED DESCRIPTION
[0042] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.
[0043] Unless otherwise specifically stated, the relative arrangement, numerical expressions and numerical values of the parts and steps set forth in these embodiments do not limit the scope of the application. Meanwhile, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to actual proportional relationships. The technology, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be considered as a part of the specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, and therefore, once a certain item is defined in an accompanying drawing, it does not need to be further discussed in subsequent drawings.
[0044] In the description of the present application, it should be understood that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present application.
[0045] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the directional words is usually based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description. Unless otherwise stated, these directional words do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the scope of protection of the present application; the directional words "inside and outside" refer to the inside and outside relative to the contour of each component itself.
[0046] In addition, the technical features involved in the different embodiments of the present application described below can be combined with each other as long as they do not conflict with each other.
[0047] like Figures 1 to 5 As shown, an embodiment of the present application provides a compressor and an air-conditioning unit having the compressor.
[0048] The compressor of the embodiment of the present application includes a rotating shaft 10, an impeller 20 and a diffuser 30. The impeller 20 is connected to the rotating shaft 10, and has an impeller inlet 22 located at the first axial end of the impeller 20 and an impeller outlet 23 located at the radial outer end of the impeller 20. The diffuser 30 is located at the radial outer side of the impeller 20, and has a diffuser flow channel 34 and a diffuser inlet 32, a diffuser outlet 33 and a noise reduction fluid inlet 35 connected to the diffuser flow channel 34. The diffuser inlet 32 is opposite to the impeller outlet 23. The noise reduction fluid inlet 35 is configured to transport liquid noise reduction fluid into the diffuser flow channel 34.
[0049] In the compressor of the embodiment of the present application, after the liquid noise reduction fluid enters the diffuser flow channel 34 through the noise reduction fluid inlet 35, it is atomized to form a mist fluid under the action of high-speed exhaust gas. The tiny droplets carried by the mist fluid can absorb the sound energy of the high-frequency noise caused by the friction of the high-speed exhaust gas, thereby achieving the purpose of reducing the operating noise of the compressor.
[0050] like Figure 2 As shown, in the compressor of some embodiments, the noise reduction fluid inlet 35 is configured to deliver the noise reduction fluid to the diffuser inlet 32 of the diffuser flow passage 34 .
[0051] Since the diffuser inlet 32 is the location where the high-speed exhaust gas flows fastest and is also the location where the high-speed exhaust gas transitions from the rotating parts to the stationary parts, the noise reduction fluid inlet 35 is configured to deliver the noise reduction fluid to the diffuser inlet 32 of the diffuser flow channel 34. Delivering the noise reduction fluid at the diffuser inlet 32 can absorb the high-frequency noise there and prevent the noise from continuing to transmit downstream, thereby achieving a better noise reduction effect.
[0052] like Figure 2 As shown, in some embodiments of the compressor, the diffuser 30 includes an axial end of the impeller 20 located away from the impeller inlet 21 (i.e., the axial second end of the diffuser flow channel 34, corresponding to Figure 2 The compressor further comprises an end wall 31 of the impeller 20 (the middle right end), and a noise reduction fluid inlet 35 is arranged on the end wall 31 to deliver the noise reduction fluid to the diffuser inlet 32 of the diffuser flow channel 34; the compressor further comprises an oil blocking sleeve 40. The oil blocking sleeve 40 is located at the axial second end of the impeller 20 and forms a gap 50 with the impeller 20, and the gap 50 is connected to the noise reduction fluid inlet 35, and the noise reduction fluid inlet 35 receives the noise reduction fluid through the gap 50.
[0053] By delivering the noise reduction fluid to the noise reduction fluid inlet 35 through the gap 50 between the impeller 20 and the oil-blocking sleeve 40, a channel for delivering the noise reduction fluid is formed inside the compressor, so that when the noise reduction fluid is delivered into the noise reduction fluid inlet 35 due to the rotation of the impeller 20, the part close to the high-speed exhaust gas forms a vortex consistent with the rotation direction of the high-speed exhaust gas, which helps to reduce the noise generated when the noise reduction fluid and the high-speed exhaust gas are mixed, thereby helping to further reduce the operating noise of the compressor.
[0054] like Figure 2 As shown, in some embodiments of the compressor, the oil blocking sleeve 40 is integrally provided with the end wall 31 ; and / or the noise reduction fluid inlet 35 is an annular opening coaxial with the impeller 20 .
[0055] The oil-blocking sleeve 40 is integrally arranged with the end wall 31, which is beneficial to preventing the noise reduction fluid from flowing from between the oil-blocking sleeve 40 and the end wall 31 to an undesirable location, such as the motor room, and is beneficial to simplifying the compressor structure. The noise reduction fluid inlet 35 is an annular opening coaxial with the impeller 20, which is beneficial for the noise reduction fluid to flow evenly to the noise reduction fluid inlet 35, thereby reducing the disturbance of the airflow at the compressor outlet 32 caused by the uneven noise reduction fluid on the basis of reducing noise.
[0056] In some embodiments of the compressor, the shaft 10 has a hollow portion 11, a shaft inlet 12 for conveying noise reduction fluid to the hollow portion 11, a shaft outlet 13 for outputting the noise reduction fluid from the hollow portion 11, and a connecting hole 14 connecting the hollow portion 11 and the shaft outlet 13, and the shaft outlet 13 is connected to the gap 50.
[0057] The shaft 10 is provided with a hollow portion 11, a shaft inlet 12, a shaft outlet 13 and a connecting hole 14. On the one hand, the noise reduction fluid can enter the gap 50 through the hollow portion 11. The noise reduction fluid can absorb the heat of the shaft 10 in the process of passing through the hollow portion 11, which has a cooling effect on the shaft 10, and is beneficial to ensuring the stability of the compressor operation; on the other hand, since the runner 10 and the impeller 20 rotate synchronously, the noise reduction fluid entering the gap 50 has a rotation direction consistent with the rotation direction of the high-speed exhaust gas, which is further beneficial to the formation of a vortex consistent with the rotation direction of the high-speed exhaust gas in the part close to the high-speed exhaust gas when the noise reduction fluid is fed into the noise reduction fluid inlet 35, so that the mist fluid can form a gradually decreasing velocity gradient consistent with the rotation direction of the high-speed exhaust gas from the high-speed exhaust gas side to the end wall 31 side along the axial direction of the impeller 20, which is beneficial to reduce the noise generated when the noise reduction fluid and the high-speed exhaust gas are mixed, thereby facilitating further reduction of the compressor operation noise.
[0058] like Figures 2 to 4 As shown, in some embodiments of the compressor, the hollow portion 11 includes a central hole arranged in the radial middle of the rotating shaft 10. The diameter of the central hole is 1 / 8 to 1 / 10 of the maximum diameter of the rotating shaft 10; and / or a turbulent structure is arranged on the hole wall of the central hole.
[0059] The hollow part 11 is set in the form of a center hole, which is conducive to the processing of the hollow part. The diameter of the center hole is set to 1 / 8 to 1 / 10 of the maximum diameter of the rotating shaft 10, which is conducive to reasonably controlling the flow of the noise reduction fluid entering the diffuser 30 through the hollow part 11 while ensuring the noise reduction and heat dissipation effects, thereby preventing this part of the noise reduction fluid from affecting the energy efficiency of the compressor. A spoiler structure is provided on the hole wall of the center hole, which is conducive to increasing the turbulence of the noise reduction fluid when it flows in the hollow part 11, thereby improving the heat exchange efficiency between the noise reduction fluid and the rotating shaft 10, and enhancing the cooling effect of the rotating shaft 10. The spoiler structure, for example, includes a protrusion, a groove and / or a rough surface provided on the hole wall of the center hole.
[0060] like Figure 5 As shown, in some embodiments of the compressor, the hollow portion 11 includes a constricted section 111 disposed at the shaft inlet 12 , and the flow area of the constricted section 111 gradually decreases from the shaft inlet 12 to a side away from the shaft inlet 12 .
[0061] The hollow portion 11 is configured to include a constricted section 111 disposed at the shaft inlet 12 . Since the constricted section 111 has a flow-guiding function, it is beneficial for the noise-reducing fluid at the shaft inlet 12 to enter the hollow portion 11 smoothly and orderly.
[0062] like Figure 3 and Figure 4 As shown, in some embodiments of the compressor, the shaft 10 includes more than two shaft outlets 13 arranged along the circumference of the shaft 10 and more than two connecting holes 14 corresponding one to the two or more shaft outlets 13; and / or the shaft outlets 13 along the axial direction of the impeller 20 are opposite to the radial inner side of the interval.
[0063] The rotating shaft 10 includes more than two rotating shaft outlets 13 and more than two connecting holes 14 arranged along the circumference of the rotating shaft 10, which is conducive to making the noise reduction fluid in the hollow part 11 enter the gap 50 more uniformly, thereby making the noise reduction fluid in the gap 50 more uniform, and then making the noise reduction fluid entering the diffuser inlet 32 more uniform, reducing the disturbance of the noise reduction fluid to the gas at the impeller outlet 23. The rotating shaft outlet 13 is opposite to the radial inner side of the gap, so that there is no need to set a flow path from the rotating shaft outlet 13 to the gap 50 for the noise reduction fluid. On the one hand, it is conducive to simplifying the structure and reducing the flow resistance of the noise reduction fluid. On the other hand, it is also conducive to making the noise reduction fluid in the hollow part 11 enter the gap 50 more uniformly, thereby making the noise reduction fluid in the gap 50 more uniform, and then making the noise reduction fluid entering the diffuser inlet 32 more uniform, reducing the disturbance of the noise reduction fluid to the high-speed exhaust gas, and helping to reduce the overall noise level when the compressor is running.
[0064] like Figure 3 and Figure 4 As shown, in some embodiments of the compressor, more than two shaft outlets 13 and more than two connecting holes 14 are evenly arranged along the circumference of the shaft 10; and / or the number of the more than two shaft outlets 13 and the more than two connecting holes 14 is greater than or equal to the number of blades 21 of the impeller 20; and / or the sum of the flow areas of the more than two shaft outlets 13 is equal to the sum of the flow areas of the center hole, and / or the sum of the flow areas of the more than two connecting holes 14 is equal to the sum of the flow areas of the center hole.
[0065] The two or more shaft outlets 13 and the two or more connecting holes 14 are evenly arranged along the circumference of the shaft 10, which is further conducive to making the noise reduction fluid in the hollow part 11 enter the interval 50 more evenly, so that the noise reduction fluid entering the diffuser inlet 32 is more even, and the disturbance of the noise reduction fluid to the gas at the impeller outlet 23 is reduced. The number of the two or more shaft outlets 13 and the two or more connecting holes 14 is greater than or equal to the number of blades 21 of the impeller 20, which is also conducive to making the noise reduction fluid in the hollow part 11 enter the interval 50 more evenly, so that the noise reduction fluid entering the diffuser inlet 32 is more even, and the disturbance of the noise reduction fluid to the gas at the impeller outlet 23 is reduced. The sum of the flow areas of the two or more connecting holes 14 is equal to the sum of the flow areas of the central hole, which is conducive to maintaining the stability of the pressure and state of the noise reduction fluid from the hollow part 11 to the interval 50, so that the pressure and state of the noise reduction fluid entering the diffuser inlet 32 are more stable, thereby reducing the disturbance of the noise reduction fluid to the gas at the impeller outlet 23.
[0066] like Figure 2 and Figure 3 As shown, in some embodiments of the compressor, the communicating hole 14 is inclined from the hollow portion 11 to the shaft outlet 13 along the direction from the axial second end to the axial first end of the shaft.
[0067] The connecting hole 14 is inclined from the hollow portion 11 to the shaft outlet 13 along the direction from the second axial end of the shaft 10 to the first axial end, which is beneficial for the fluid in the hollow portion 11 to smoothly enter the connecting hole 14 along the flow direction of the noise reduction fluid, and smoothly enter the gap 50 through the connecting hole 14, so that the noise reduction fluid enters the gap 50 in rotation with the rotation of the shaft 10, reducing the direct impact between the noise reduction fluid entering the gap 50 and the stationary oil-blocking sleeve 40, which is beneficial to reducing the overall noise level when the compressor is running.
[0068] In the compressor of some embodiments, the angle β between the communicating hole 14 and the axis of the rotating shaft 10 is greater than or equal to 80° and less than 90°.
[0069] The angle β between the connecting hole 14 and the axis of the rotating shaft 10 is greater than or equal to 80° and less than 90°, which helps prevent the noise reduction fluid from excessively impacting the end face of the second axial end of the impeller 20, thereby reducing the impact noise generated thereby and helping to reduce the overall noise level when the compressor is running.
[0070] like Figure 5 As shown, in some embodiments of the compressor, the impeller 20 is arranged at the first axial end of the rotating shaft 10, and the rotating shaft inlet 12 is arranged on the end surface of the second axial end of the rotating shaft 10; the compressor also includes an end cover 60, which is rotatable relative to the rotating shaft 10 and is covered at the rotating shaft inlet 12, and the end cover 60 is provided with a port 63 connected to the rotating shaft inlet 12, and a sealing structure 64 is provided between the end cover 60 and the rotating shaft 10.
[0071] The end cover 60 can be provided to better realize a relatively rotatable sealed connection between the rotating shaft 10 and the stationary fluid conveying part (such as the conduit 9 described later) for introducing the noise reduction fluid into the hollow portion 11 .
[0072] like Figure 5 As shown, in some embodiments of the compressor, the end cover 60 includes an end wall 61 and a side wall 62 connected to the outer periphery of the end wall 61, the port 63 is arranged on the end wall 61, the side wall 62 is sleeved on the axial second end of the rotating shaft 10, and the sealing structure 64 is arranged on the side wall 62.
[0073] The end cover 60 includes an end wall 61 and a side wall 62, and a port 63 and a sealing structure 64 are respectively arranged on the end wall 61 and the side wall 62, so that the connection and sealing of the end cover 60 and the rotating shaft 10 and the connection of the end cover 60 and the fluid conveying part are simple, convenient and effective. The sealing structure 64 is, for example, a comb-teeth sealing structure arranged on the radial inner side of the side wall 62.
[0074] In the compressor of some embodiments, a buffer chamber C communicating with the port 63 and the shaft inlet 12 is formed between the end cover 60 and the shaft 10 .
[0075] A buffer chamber C is formed between the end cover 60 and the shaft 10, which helps to make the parameters of the noise reduction fluid entering the shaft inlet 12 relatively stable or change smoothly, that is, it helps to make the parameters of the noise reduction fluid entering the diffuser flow channel 34 of the diffuser 30 relatively stable or change smoothly, thereby helping to reduce unnecessary disturbances to the high-speed exhaust caused by drastic changes in the parameters of the noise reduction fluid introduced from the port 63.
[0076] An embodiment of the present application also provides an air-conditioning unit, which includes a compressor 1, a condenser 2, a throttling device 3 and an evaporator 4 connected as a refrigerant circuit through a refrigerant pipeline 5; the compressor 1 is the compressor 1 of the embodiment of the present application; the air-conditioning unit also includes a conduit 9, and the noise reduction fluid inlet 35 receives the liquid refrigerant in the condenser 2 as a noise reduction fluid through the conduit 9.
[0077] The air conditioning unit includes the compressor of the embodiment of the present application, and thus has the effect of the compressor of the embodiment of the present application. In addition, the liquid refrigerant in the condenser 2 is transported to the noise reduction fluid inlet 35 through the conduit 9, and the high-pressure liquid refrigerant encounters the high-speed exhaust gas in the diffuser flow channel 34 to form a mist fluid, which can absorb the sound energy of the high-frequency noise caused by the friction of the high-speed exhaust gas, thereby achieving the purpose of reducing the operating noise of the compressor.
[0078] The following combination Figures 1 to 5 The compressor and the air conditioning unit of the embodiment of the present application are described in more detail. In the following description, the "axial first end" refers to Figures 2 to 5 The left end in the figure, “the second axial end” refers to Figures 2 to 5 The right end of .
[0079] like Figure 1 As shown, the air conditioning unit includes a compressor 1, a condenser 2, a throttling device 3 and an evaporator 4 connected as a refrigerant circuit through a refrigerant pipeline 5. The air conditioning unit also includes a conduit 9, and the noise reduction fluid inlet 35 receives the liquid refrigerant in the condenser 2 as the noise reduction fluid through the conduit 9. Figure 1 and Figure 5 As shown, the conduit 9 is connected between the condenser 2 and the shaft inlet 12 of the shaft 10 of the compressor 1 .
[0080] Refrigerants of different forms flow in the refrigerant circuit. Compressor 1 compresses the low-temperature and low-pressure gas output from evaporator 4 to form high-pressure exhaust gas. The high-pressure exhaust gas is mixed with the low-temperature and high-pressure liquid drawn from condenser 2 to form high-temperature and high-pressure gas, which is transported to condenser 2. Condenser 2 condenses the high-temperature and high-pressure gas into low-temperature and high-pressure liquid, which is throttled and depressurized by throttling device 3 to form a low-temperature and low-pressure gas-liquid mixture, which is transported to evaporator 4. The evaporator 4 evaporates the low-temperature and low-pressure gas to compressor 1, completing the refrigerant cycle.
[0081] like Figure 2 As shown, the compressor 1 includes a rotating shaft 10 , an impeller 20 , a diffuser 30 , an oil blocking sleeve 40 , a fluid flow channel 50 , an end cover 60 , a motor 70 , a bearing seat 80 , a bearing 90 and a housing 100 .
[0082] The impeller 20 is connected to the first axial end of the rotating shaft 10. The end cover 60 is installed at the second axial end of the rotating shaft 10. The motor 70 is installed on the rotating shaft 10 and is located between the impeller 20 and the end cover 60. The housing 100 covers the outside of the motor 70. Two bearing seats 80 are respectively arranged at the axial ends of the motor 70 and connected to the housing 100. Two bearings 90 are respectively installed in the two bearing seats 80. The rotating shaft 10 is rotatably supported on the two bearing seats 80 through the two bearings 90.
[0083] The impeller 20 includes a plurality of blades 21. An impeller inlet 22 is provided at a first axial end of the impeller 20, and an impeller outlet 23 is provided at a radially outer end of the impeller 20.
[0084] The rotating shaft 10 includes a central hole as a hollow portion 11 , a rotating shaft inlet 12 , a plurality of communication holes 14 , and a plurality of rotating shaft outlets 13 .
[0085] The center hole is a blind hole opened at the second axial end of the rotating shaft 10. The opening at the second axial end forms the rotating shaft inlet 12. The diameter of the center hole is 1 / 8 to 1 / 10 of the maximum diameter of the rotating shaft 10, for example, 1 / 9. A plurality of protrusions (not shown) as flow-turbine structures are provided on the hole wall of the center hole. The second axial end of the center hole includes a constricted section 111 provided at the rotating shaft inlet 12. The flow area of the constricted section 111 gradually decreases from the rotating shaft inlet 12 to the side away from the rotating shaft inlet 12.
[0086] like Figure 2 and Figure 3 As shown, a plurality of connecting holes 14 are arranged one by one with a plurality of rotating shaft outlets 13 and are evenly distributed along the circumference of the rotating shaft 10. Each connecting hole 14 connects the central hole with the corresponding rotating shaft outlet 13. The connecting holes 14 are inclined from the hollow portion 11 to the rotating shaft outlet 13 along the direction from the axial second end of the rotating shaft to the axial first end. The angle β between the connecting hole 14 and the axis of the rotating shaft 10 is greater than or equal to 80° and less than 90°, for example, it can be 80°, 82.5°, 85°, 89°, etc.
[0087] The number of the plurality of shaft outlets 13 and the plurality of communication holes 14 is equal to the number of blades 21 of the impeller 20. The sum of the cross-sectional areas of the plurality of communication holes 14 is equal to the sum of the cross-sectional areas of the central hole, so that the sum of the flow areas of the communication holes 14 is equal to the sum of the flow areas of the central hole.
[0088] The diffuser 30 is located radially outside the impeller 20. The diffuser 30 includes two opposite end walls, and a diffuser flow channel 34 is formed between the two end walls. A diffuser inlet 32 is formed radially inside the diffuser flow channel 34, and the diffuser inlet 32 is opposite to the impeller outlet. A diffuser outlet 33 is formed radially outside the diffuser flow channel 34. The noise reduction gas inlet 35 is an annular opening coaxial with the impeller 20, formed on the end wall 31 of the diffuser 30 on the side away from the axial first end of the impeller 20 and close to the diffuser inlet 32 along the radial direction of the impeller 20.
[0089] The oil-blocking sleeve 40 is located at the radial inner side of the end plate 31 and is integrally provided with the end plate 31 of the diffuser 30. The oil-blocking sleeve 40 is located at the axial second end of the impeller 20 and has a gap 50 with the end surface of the axial second end of the impeller 20. The gap 50 is respectively connected to the plurality of shaft outlets 13 and the noise reduction fluid inlet 35. The noise reduction fluid inlet 35 receives the noise reduction fluid through the gap 50. The plurality of shaft outlets 13 are opposite to the radial inner side of the gap forming the gap 50.
[0090] The end cover 60 and the rotating shaft 10 are rotatably mounted at the rotating shaft inlet 12. The end cover 60 is provided with a port 63 connected to the rotating shaft inlet 12. A comb-teeth sealing structure as a sealing structure 64 is provided between the end cover 60 and the rotating shaft 10. The comb-teeth sealing structure can prevent leakage of the noise reduction fluid without affecting the rotation of the rotating shaft 10.
[0091] The end cover 60 includes an end wall 61 and a side wall 62 connected to the outer periphery of the end wall 61. The port 63 is arranged in the radial middle of the end wall 61. The side wall 62 is sleeved on the axial second end of the rotating shaft 10. The comb seal structure is arranged on the radial inner side of the side wall 62. The end wall 61 is spaced from the end surface of the axial second end of the rotating shaft 10, so that a buffer chamber C connecting the port 63 and the rotating shaft inlet 12 is formed between the end cover 60 and the rotating shaft 10.
[0092] In the air-conditioning unit of the embodiment of the present application, the rotating shaft 10 of the compressor 1 has a center hole. The high-pressure liquid refrigerant serving as the noise reduction fluid can be introduced from the condenser into the buffer chamber C through the conduit 9 connected to the port 63 of the end cover 60, and then enters the rotating shaft inlet 12 at the second axial end of the rotating shaft 10. After that, the noise reduction fluid flows through the center hole serving as the hollow portion 11, multiple connecting holes 14, multiple rotating shaft outlets 13 and enters the interval 50 in sequence. Under the rotation of the rotating shaft 10 and the impeller 20, the noise reduction fluid is centrifugal force, the pressure of the noise reduction fluid itself, and the high pressure at the impeller outlet 23 of the impeller 20. The exhaust gas suction force enters the diffuser inlet 32 of the diffuser flow channel 34 from the noise reduction fluid inlet 35 provided on the end plate 31 at the radial outer end of the oil-blocking sleeve 40. On the one hand, the high-pressure liquid refrigerant flows in the center hole of the rotating shaft 10 to take away the heat generated by the rotating shaft 10 during operation, thereby ensuring the stability of the operation of the compressor 1. On the other hand, the high-pressure liquid refrigerant meets the high-temperature exhaust gas at the impeller outlet 23 to form a mist fluid. The mist fluid absorbs the sound energy of the high-frequency noise caused by the friction of the high-speed exhaust gas, thereby achieving the purpose of reducing the operating noise of the compressor 1. The refrigerant flows in the compressor in the following direction: Figure 1 and Figure 2 Therefore, the compressor and air conditioning unit of the embodiment of the present application can reduce the temperature of the rotating shaft of the compressor while reducing the noise of the compressor during operation, and there is no need to introduce a new power device for conveying the noise reduction fluid, which is conducive to reducing the complexity and energy consumption of the compressor caused by introducing the noise reduction fluid into the diffuser.
[0093] Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the present application and not to limit it. Although the present application has been described in detail with reference to the preferred embodiments, ordinary technicians in the relevant field should understand that the specific implementation methods of the present application can still be modified or some technical features can be replaced by equivalents, which should all be included in the scope of the technical solution requested for protection in this application.
Claims
1. A compressor, characterized in that: include: Axis (10); an impeller (20) connected to the rotating shaft (10), having an impeller inlet (22) located at an axial first end of the impeller (20) and an impeller outlet (23) located at a radial outer end of the impeller (20); and The diffuser (30) is located radially outside the impeller (20), and has a diffuser flow channel (34) and a diffuser inlet (32), a diffuser outlet (33) and a noise reduction fluid inlet (35) connected to the diffuser flow channel (34). The diffuser inlet (32) is opposite to the impeller outlet (23), and the noise reduction fluid inlet (35) is configured to transport liquid noise reduction fluid into the diffuser flow channel (34).
2. The compressor according to claim 1, characterized in that The noise reduction fluid inlet (35) is configured to deliver the noise reduction fluid to the diffuser inlet (32) of the diffuser flow channel (34).
3. The compressor according to claim 1, characterized in that The diffuser (30) comprises an end wall (31) located at an end away from the impeller inlet (21) along the axial direction of the impeller (20), and the noise reduction fluid inlet (35) is arranged on the end wall (31); The compressor further comprises an oil-blocking sleeve (40), the oil-blocking sleeve (40) being located at the second axial end of the impeller (20) and having a gap (50) with the end surface of the second axial end of the impeller (20), the gap (50) being in communication with the noise reduction fluid inlet (35), and the noise reduction fluid inlet (35) receiving the noise reduction fluid through the gap (50).
4. The compressor according to claim 3, characterized in that The oil-blocking sleeve (40) is integrally provided with the end wall (31); and / or The noise reduction fluid inlet (35) is an annular opening coaxial with the impeller (20).
5. The compressor according to claim 3, characterized in that The rotating shaft (10) comprises a hollow portion (11), a rotating shaft inlet (12) for conveying the noise reduction fluid into the hollow portion (11), a rotating shaft outlet (13) for outputting the noise reduction fluid from the hollow portion (11), and a connecting hole (14) connecting the hollow portion (11) and the rotating shaft outlet (13), wherein the rotating shaft outlet (13) is connected to the spacer (50).
6. The compressor according to claim 5, characterized in that The hollow portion (11) comprises a central hole arranged in the radial middle of the rotating shaft (10), wherein The diameter of the central hole is 1 / 8 to 1 / 10 of the maximum diameter of the rotating shaft (10); and / or A flow-disturbing structure is arranged on the hole wall of the central hole.
7. The compressor according to claim 5, characterized in that The hollow portion (11) comprises a constricted section (111) provided at the rotating shaft inlet (12), wherein the flow area of the constricted section (111) gradually decreases from the rotating shaft inlet (12) to a side away from the rotating shaft inlet (12).
8. The compressor according to claim 5, characterized in that The rotating shaft (10) comprises at least two rotating shaft outlets (13) arranged along the circumference of the rotating shaft (10) and at least two communicating holes (14) corresponding one-to-one to the at least two rotating shaft outlets (13); and / or Along the axial direction of the impeller (20), the shaft outlet (13) is opposite to the radial inner side of the spacer (50).
9. The compressor according to claim 8, characterized in that The two or more rotating shaft outlets (13) and the two or more communicating holes (14) are evenly arranged along the circumference of the rotating shaft (10); and / or The number of the two or more rotating shaft outlets (13) and the two or more communicating holes (14) is greater than or equal to the number of blades (21) of the impeller (20); and / or The sum of the flow areas of the two or more rotating shaft outlets (13) is equal to the sum of the flow areas of the central hole, and / or the sum of the flow areas of the two or more connecting holes (14) is equal to the sum of the flow areas of the central hole.
10. The compressor according to claim 5, characterized in that The communicating hole (14) is inclined from the hollow portion (11) to the rotating shaft outlet (13) along a direction from the axial second end to the axial first end of the rotating shaft.
11. The compressor according to claim 10, characterized in that The included angle (β) between the connecting hole (14) and the axis of the rotating shaft (10) is greater than or equal to 80° and less than 90°.
12. The compressor according to any one of claims 5 to 11, characterized in that The impeller (20) is arranged at a first axial end of the rotating shaft (10), and the rotating shaft inlet (12) is arranged at an end surface of a second axial end of the rotating shaft (10); The compressor further comprises an end cover (60), the end cover (60) and the rotating shaft (10) being rotatably arranged at the rotating shaft inlet (12), the end cover (60) being provided with a port (63) communicating with the rotating shaft inlet (12), and a sealing structure (64) being provided between the end cover (60) and the rotating shaft (10).
13. The compressor according to claim 12, characterized in that The end cover (60) comprises an end wall (61) and a side wall (62) connected to the outer periphery of the end wall (61); the port (63) is arranged on the end wall (61); the side wall (62) is sleeved on the second axial end of the rotating shaft (10); and the sealing structure (64) is arranged on the side wall (62).
14. The compressor according to claim 13, characterized in that A buffer chamber (C) communicating with the port (63) and the rotating shaft inlet (12) is formed between the end cover (60) and the rotating shaft (10).
15. An air conditioning unit, comprising a compressor (1), a condenser (2), a throttling device (3) and an evaporator (4) connected to form a refrigerant circuit via a refrigerant pipeline (5), characterized in that: The compressor (1) is the compressor (1) according to any one of claims 1 to 14; The air conditioning unit further comprises a conduit (9), and the noise reduction fluid inlet (35) receives the liquid refrigerant in the condenser (2) as the noise reduction fluid through the conduit (9).