Compressor and air conditioning unit

Abstract

The utility model provides a compressor and an air conditioning unit. The compressor includes: a rotating shaft; the impeller is connected to the rotating shaft and provided with an impeller inlet located at the first axial end of the impeller and an impeller outlet located at the radial outer end of the impeller; the diffuser is located on the radial outer side of the impeller and comprises a diffuser end wall located at the end, away from the impeller inlet, in the axial direction of the impeller, the diffuser is provided with a diffusion flow channel, a diffuser inlet, a diffuser outlet and a noise reduction fluid inlet, the diffuser inlet communicates with the diffusion flow channel, the diffuser inlet is opposite to the impeller outlet, and the noise reduction fluid inlet is formed in the diffuser end wall; and a noise reduction valve configured to deliver a noise reduction fluid to a diffuser inlet of the diffuser flow passage. The air conditioning unit comprises the compressor.

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 conditioners, generate considerable noise during operation. The primary source of noise is the refrigeration compressor. When the compressor is operating, refrigerant gas is drawn in through the intake pipe and enters the rotating impeller through the impeller inlet. Due to the high-speed rotation of the impeller, the blades propel the refrigerant gas along the impeller's flow path from the center toward the radially outer end. Ultimately, as the gas flows out of the impeller outlet at the radially outer end, both the pressure and absolute velocity of the refrigerant gas increase, resulting in high-speed exhaust. This high-speed exhaust gas flows into the diffuser, generating noise, which is the primary source of compressor noise.

[0003] The above statements are only used to provide background technical information related to the present application and do not necessarily constitute prior art. Utility Model Content

[0004] The purpose of this 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] In a first aspect, 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 a diffuser end wall located at one end away from the impeller inlet along the axial direction of the impeller, and the noise reduction fluid inlet is arranged on the diffuser 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 diffuser end wall; and / or the noise reduction fluid inlet is an annular opening coaxial with the impeller.

[0009] In some embodiments of the compressor, the rotating shaft has a hollow portion, a rotating shaft inlet for delivering the noise reduction fluid to the hollow portion, a rotating shaft outlet for outputting the noise reduction fluid from the hollow portion, and a communication hole communicating the hollow portion with the rotating shaft outlet, the rotating shaft outlet being in communication with the gap.

[0010] In some embodiments of the compressor, the hollow portion comprises a central hole arranged at a radial middle portion of the rotating shaft, wherein a diameter of the central hole is 1 / 8 to 1 / 10 of a maximum diameter of the rotating shaft; and / or a hole wall of the central hole is provided with a turbulence structure.

[0011] In some embodiments of the compressor, the hollow portion comprises a necked portion arranged at the rotating shaft inlet, the necked portion gradually reducing a flow area from the rotating shaft inlet to a side away from the rotating shaft inlet.

[0012] In some embodiments of the compressor, the rotating shaft comprises two or more rotating shaft outlets arranged along a circumferential direction of the rotating shaft and two or more communication holes corresponding to the two or more rotating shaft outlets one by one; and / or the rotating shaft outlets are opposite to a radially inner side of the gap along an axial direction of the impeller.

[0013] In some embodiments of the compressor, the two or more rotating shaft outlets and the two or more communication holes are uniformly arranged along the circumferential direction of the rotating shaft; and / or a number of the two or more rotating shaft outlets and the two or more communication holes is greater than or equal to a number of blades of the impeller; and / or a sum of flow areas of the two or more rotating shaft outlets is equal to a sum of flow areas of the central hole, and / or a sum of flow areas of the two or more communication holes is equal to the sum of flow areas of the central hole.

[0014] In some embodiments of the compressor, the communication hole is inclined from the hollow portion to the rotating shaft outlet in a direction from an axial second end to an axial first end of the rotating shaft.

[0015] In some embodiments of the compressor, an included angle between the communication hole and an 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 an axial first end of the rotating shaft, and the rotating shaft inlet is arranged at an end face of an axial second end of the rotating shaft; the compressor further comprises an end cover, the end cover being rotatably covered at the rotating shaft inlet relative to the rotating shaft, the end cover being provided with a port in communication with the rotating shaft inlet, and a sealing structure being arranged between the end cover and the rotating shaft.

[0017] In some embodiments of the compressor, the end cover comprises an end cover end wall and a side wall connected to the periphery of the end cover end wall, the port is arranged on the end cover 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 some embodiments of the compressor, a buffer cavity is formed between the end cover and the rotating shaft, and the buffer cavity communicates the port and the inlet of the rotating shaft.

[0019] The second aspect of the present application provides an air conditioning unit, which comprises a compressor, a condenser, a throttling device and an evaporator connected as a refrigerant circuit through refrigerant pipelines; the compressor is the compressor of the first aspect; the air conditioning unit further comprises a conduit, and the noise reduction fluid inlet receives liquid refrigerant in the condenser as the noise reduction fluid through the conduit.

[0020] Based on the compressor provided by the present application, the liquid noise reduction fluid enters the diffuser passage through the noise reduction fluid inlet, and is atomized into misty fluid under the action of high-speed exhaust gas. The misty fluid carries small droplets that can absorb the sound energy of high-frequency noise caused by friction of high-speed exhaust gas, so as to achieve the purpose of reducing the operating noise of the compressor.

[0021] The air conditioning unit of the embodiments of the present application has the advantages of the compressor of the embodiments of the present application.

[0022] Other features and advantages of the present application will become apparent from the following detailed description of exemplary embodiments thereof, with reference to the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0023] The accompanying drawings, which are included to provide a further understanding of the present application, constitute a part of the present application, and the illustrative embodiments of the present application and their description serve to explain the present application, and do not constitute improper limitations on the present application. In the drawings:

[0024] Figure 1 It is a schematic diagram of the principle of the air conditioning unit of some embodiments of the present application.

[0025] Figure 2 It is a schematic diagram of the principle of the compressor of some embodiments of the present application.

[0026] Figure 3 It is a schematic diagram of the structure of the combination structure of the rotating shaft and the end cover and the conduit of the compressor of some embodiments of the present application.

[0027] Figure 4 It is a schematic diagram of the structure of the combination structure of the rotating shaft and the end cover and the conduit of the compressor of some embodiments of the present application. Figure 3 It is a schematic diagram of the structure of the combination structure of the rotating shaft and the end cover and the conduit of the compressor of some embodiments of the present application.

[0028] Figure 5 It is a schematic diagram of the structure of the combination structure of the rotating shaft and the end cover and the conduit of the compressor of some embodiments of the present application. Figure 3Structure diagram of the end cover of the combination structure shown.

[0029] Figures 1 to 5 In the drawings, reference numerals respectively represent:

[0030] 1. Compressor

[0031] 2. Condenser

[0032] 3. Throttling device

[0033] 4. Evaporator

[0034] 5. Refrigerant pipeline

[0035] 9. Conduit

[0036] 10. Rotation shaft; 11. Hollow part; 111. Necked section; 12. Rotation shaft inlet; 13. Rotation shaft outlet; 14. Communication pipe

[0037] 20. Impeller; 21. Blade; 22. Impeller inlet; 23. Impeller outlet

[0038] 30. Diffuser; 31. Diffuser end wall; 32. Diffuser inlet; 33. Diffuser outlet; 34. Diffuser flow channel; 35. Noise reduction fluid inlet

[0039] 40. Oil blocking sleeve

[0040] 50. Interval

[0041] 60. End cover; 61. End cover end wall; 62. Side wall; 63. Port; 64. Sealing structure; C. Buffer cavity DETAILED DESCRIPTION

[0042] The technical solutions in the embodiments of the present application will be described clearly and completely below in combination with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. The description of the at least one exemplary embodiment is actually only illustrative, but not as any limitation on the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0043] The foregoing is considered as illustrative only of the principles of the application. Other variations and modifications can be made to the embodiments disclosed in this document, by persons with ordinary skill in the art, without departing from the scope of the present application, as defined in the appended claims. Furthermore, the above-described embodiments of the application can be implemented in any of a variety of contexts and architectures. Therefore, the application is not limited to the above-described embodiments, but rather only by the following claims.

[0044] In the description of the application, it needs to be understood that the words "first", "second", etc. are used to distinguish the components only for the convenience of distinguishing the corresponding components, and have no special meaning unless otherwise stated, and therefore cannot be understood as a limitation on the scope of protection of the application.

[0045] In the description of the application, it needs to be understood that the orientation or position relationship indicated by the orientation words is generally based on the orientation or position relationship shown in the drawings, and is only for the convenience of describing the application and simplifying the description, and in the absence of the opposite description, these orientation words do not indicate and imply that the devices or elements referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the scope of protection of the application; the orientation words "inner, outer" refer to the inner and outer of the contour of each component itself.

[0046] In addition, the technical features involved in different embodiments of the application described below can be combined with each other as long as there is no conflict.

[0047] As Figures 1 to 5 The compressor and air conditioning unit with the compressor are provided by the embodiments of the application.

[0048] The compressor of the embodiments of the application comprises 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 at an axial first end of the impeller 20 and an impeller outlet 23 at a radial outer end of the impeller 20. The diffuser 30 is located radially outside the impeller 20 and has a diffuser flow channel 34, a diffuser inlet 32, a diffuser outlet 33 and a noise reduction fluid inlet 35 in communication with 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 deliver liquid noise reduction fluid into the diffuser flow channel 34.

[0049] In the compressor of the embodiment, the liquid noise reduction fluid enters the diffuser passage 34 through the noise reduction fluid inlet 35, and is atomized into mist under the action of high-speed exhaust gas, so that the mist carries the sound energy of high-frequency noise caused by the friction of high-speed exhaust gas, thereby achieving the purpose of reducing the operating noise of the compressor.

[0050] As shown in Figure 2 , in some embodiments of the compressor, the noise reduction fluid inlet 35 is configured to deliver the noise reduction fluid to the diffuser inlet 32 of the diffuser passage 34.

[0051] Since the diffuser inlet 32 is the position with the fastest flow rate of high-speed exhaust gas, and is also the position where the high-speed exhaust gas transitions from the rotating member to the stationary member, the noise reduction fluid inlet 35 is configured to deliver the noise reduction fluid to the diffuser inlet 32 of the diffuser passage 34, which can absorb the high-frequency noise at the diffuser inlet 32 and prevent the noise from continuing to propagate downstream, thus achieving better noise reduction effect.

[0052] As shown in Figure 2 , in some embodiments of the compressor, the diffuser 30 includes a diffuser end wall 31 located at an end away from the impeller inlet 22 in the axial direction of the impeller 20 (i.e., the axial second end of the diffuser passage 34, corresponding to the right end in Figure 2 ), and the noise reduction fluid inlet 35 is arranged on the diffuser end wall 31 to deliver the noise reduction fluid to the diffuser inlet 32 of the diffuser passage 34; the compressor further includes 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 in communication with 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 the part of the noise reduction fluid close to the high-speed exhaust gas when it is sent into the noise reduction fluid inlet 35 by the rotation of the impeller 20 forms a rotational flow in the same direction as the rotation direction of the high-speed exhaust gas, which is beneficial to reducing the noise generated when the noise reduction fluid mixes with the high-speed exhaust gas, thereby further reducing the operating noise of the compressor.

[0054] As shown in Figure 2 , in some embodiments of the compressor, the oil blocking sleeve 40 is integrally arranged with the diffuser end wall 31; and / or the noise reduction fluid inlet 35 is an annular port coaxial with the impeller 20.

[0055] The oil-blocking sleeve 40 is integrally formed with the diffuser end wall 31, preventing the noise-reduction fluid from flowing between the oil-blocking sleeve 40 and the diffuser end wall 31 to undesirable locations, such as the motor chamber, and simplifying the compressor structure. The noise-reduction fluid inlet 35 is an annular opening coaxial with the impeller 20, facilitating uniform flow of the noise-reduction fluid to the inlet 35. This, in turn, reduces noise while minimizing disturbances to the airflow at the compressor outlet 32 ​​caused by uneven distribution of the noise-reduction fluid.

[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, which is further beneficial to the formation of a vortex consistent with the rotation direction of the high-speed exhaust when the noise reduction fluid is fed into the noise reduction fluid inlet 35, thereby forming a vortex consistent with the rotation direction of the high-speed exhaust in the part close to the high-speed exhaust. Therefore, a gradually decreasing velocity gradient consistent with the rotation direction of the high-speed exhaust can be formed along the axial direction of the impeller 20 from the high-speed exhaust side to the diffuser end wall 31 side, which is beneficial to reducing the noise generated when the noise reduction fluid and the high-speed exhaust are mixed, thereby further reducing the operating noise of the compressor.

[0058] like Figures 2 to 4 As shown, in some embodiments of the compressor, the hollow portion 11 includes a central hole provided 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 flow-turbine structure is provided on the hole wall of the central hole.

[0059] The hollow portion 11 is configured as a center hole, which facilitates processing of the hollow portion. The diameter of the center hole is configured to be 1 / 8 to 1 / 10 of the maximum diameter of the rotating shaft 10, which facilitates reasonable control of the flow rate of the noise reduction fluid entering the diffuser 30 through the hollow portion 11 while ensuring noise reduction and heat dissipation effects, thereby preventing this portion of the noise reduction fluid from affecting the energy efficiency of the compressor. A flow disturbance structure is provided on the wall of the center hole, which facilitates increasing the turbulence of the noise reduction fluid when it flows in the hollow portion 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 flow disturbance structure, for example, includes protrusions, grooves, and / or rough surfaces provided on the 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 provided at the shaft inlet 12 , and the flow area of ​​the constricted section 111 gradually decreases from the shaft inlet 12 to the side away from the shaft inlet 12 .

[0061] The hollow portion 11 is configured to include a constricted section 111 provided at the shaft inlet 12 . Since the constricted section 111 has a flow-guiding function, it is beneficial for the noise reduction 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 two or more shaft outlets 13 arranged along the circumference of the shaft 10 and two or more connecting holes 14 corresponding one-to-one to the two or more shaft outlets 13; and / or the shaft outlet 13 along the axial direction of the impeller 20 is opposite to the radial inner side of the interval.

[0063] The shaft 10 includes two or more shaft outlets 13 and two or more communicating holes 14 arranged along its circumference. These facilitate relatively uniform flow of the noise reduction fluid within the hollow portion 11 into the gap 50, thereby ensuring a more uniform flow of the noise reduction fluid within the gap 50 and, in turn, ensuring a more uniform flow of the noise reduction fluid into the diffuser inlet 32, thus reducing disturbances caused by the noise reduction fluid to the gas at the impeller outlet 23. The shaft outlets 13 face the radially inner side of the gap, eliminating the need for a dedicated flow path from the shaft outlet 13 to the gap 50. This simplifies the structure and reduces flow resistance of the noise reduction fluid. Furthermore, it also facilitates relatively uniform flow of the noise reduction fluid within the hollow portion 11 into the gap 50, thereby ensuring a more uniform flow of the noise reduction fluid within the gap 50 and, in turn, ensuring a more uniform flow of the noise reduction fluid into the diffuser inlet 32, thus reducing disturbances caused by the noise reduction fluid to the high-speed exhaust gas and, consequently, reducing the overall noise level during compressor operation.

[0064] like Figure 3 and Figure 4 As shown, in some embodiments of the compressor, 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; and / or 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; and / or the sum of the flow areas of the two or more 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 two or more 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 communication holes 14 are uniformly arranged along the circumference of the shaft 10, which further facilitates the noise reduction fluid in the hollow portion 11 to enter the interval 50 more uniformly, so as to facilitate the noise reduction fluid entering the diffuser inlet 32 to be more uniform, and reduce the disturbance of the noise reduction fluid to the gas at the impeller outlet 23. The number of the two or more shaft outlets 13 and the two or more communication holes 14 is greater than or equal to the number of the blades 21 of the impeller 20, which also facilitates the noise reduction fluid in the hollow portion 11 to enter the interval 50 more uniformly, so as to facilitate the noise reduction fluid entering the diffuser inlet 32 to be more uniform, and reduce the disturbance of the noise reduction fluid to the gas at the impeller outlet 23. The sum of the flow areas of the two or more communication holes 14 is equal to the sum of the flow areas of the central holes, which facilitates the pressure and state of the noise reduction fluid from the hollow portion 11 to the interval 50 to be maintained stable, so as to facilitate the pressure and state of the noise reduction fluid entering the diffuser inlet 32 to be more stable, thereby reducing the disturbance of the noise reduction fluid to the gas at the impeller outlet 23.

[0066] As shown in FIG. 1, in some embodiments of the compressor, the communication hole 14 is inclined from the hollow portion 11 to the shaft outlet 13 in a direction from the axial second end of the shaft to the axial first end. Figure 2 Figure 3 As shown in FIG. 1, in some embodiments of the compressor, the communication hole 14 is inclined from the hollow portion 11 to the shaft outlet 13 in a direction from the axial second end of the shaft to the axial first end.

[0067] The communication hole 14 is inclined from the hollow portion 11 to the shaft outlet 13 in a direction from the axial second end of the shaft 10 to the axial first end, which facilitates the fluid in the hollow portion 11 to smoothly enter the communication hole 14 along the flow direction of the noise reduction fluid, and to smoothly pass through the communication hole 14 to enter the interval 50, so that the noise reduction fluid rotates into the interval 50 along with the rotation of the shaft 10, reduces the direct impact of the noise reduction fluid entering the interval 50 to the stationary oil blocking sleeve 40, and facilitates reducing the overall noise level when the compressor is running.

[0068] In some embodiments of the compressor, the angle β between the communication hole 14 and the axis of the shaft 10 is greater than or equal to 80° and less than 90°.

[0069] The angle β between the communication hole 14 and the axis of the shaft 10 is greater than or equal to 80° and less than 90°, which facilitates preventing the noise reduction fluid from excessively impacting the end face of the axial second end of the impeller 20, thereby reducing the impact noise generated thereby, and facilitates reducing the overall noise level when the compressor is running.

[0070] As shown in FIG. 1, in some embodiments of the compressor, the impeller 20 is arranged at the axial first end of the shaft 10, and the shaft inlet 12 is arranged at the end face of the axial second end of the shaft 10; the compressor further comprises an end cover 60, the end cover 60 is relatively rotatable with the shaft 10 and covers the shaft inlet 12, the end cover 60 is provided with a port 63 in communication with the shaft inlet 12, and a sealing structure 64 is arranged between the end cover 60 and the shaft 10. Figure 5 As shown in FIG. 1, in some embodiments of the compressor, the impeller 20 is arranged at the axial first end of the shaft 10, and the shaft inlet 12 is arranged at the end face of the axial second end of the shaft 10; the compressor further comprises an end cover 60, the end cover 60 is relatively rotatable with the shaft 10 and covers the shaft inlet 12, the end cover 60 is provided with a port 63 in communication with the shaft inlet 12, and a sealing structure 64 is arranged between the end cover 60 and the shaft 10.​

[0071] The provision of the end cap 60 can better achieve a relatively rotatable sealed connection between the rotating shaft 10 and the stationary fluid conveying portion (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 cover end wall 61 and a side wall 62 connected to the outer periphery of the end cover end wall 61, the port 63 is arranged on the end cover 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 cap 60 includes an end cap end wall 61 and a side wall 62, with ports 63 and a sealing structure 64 disposed on the end cap end wall 61 and the side wall 62, respectively. This makes the connection and sealing between the end cap 60 and the rotating shaft 10, as well as the connection between the end cap 60 and the fluid conveying portion, simple, convenient, and effective. The sealing structure 64 is, for example, a comb-shaped sealing structure disposed radially inwardly 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 rotating shaft 10, which helps to make the parameters of the noise reduction fluid entering the rotating 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] This air conditioning unit includes the compressor of the embodiment of the present application and thus has the effects 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 via the conduit 9. The high-pressure liquid refrigerant encounters the high-speed exhaust gas in the diffuser flow channel 34 and forms a mist fluid. The mist fluid absorbs the acoustic 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 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 toFigures 2 to 5 The right end of the .

[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 via a refrigerant pipe 5. The air conditioning unit also includes a conduit 9, through which the noise reduction fluid inlet 35 receives the liquid refrigerant in the condenser 2 as the noise reduction fluid. 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] Refrigerant in different forms flows in the refrigerant circuit. Compressor 1 compresses the low-temperature, low-pressure gas output from evaporator 4 to form high-pressure exhaust gas. The high-pressure exhaust gas is mixed with the low-temperature, high-pressure liquid drawn from condenser 2 to form high-temperature, high-pressure gas, which is then transported to condenser 2. Condenser 2 condenses the high-temperature, high-pressure gas into low-temperature, high-pressure liquid. The liquid is throttled and depressurized by throttling device 3 to form a low-temperature, low-pressure gas-liquid mixture, which is then transported to evaporator 4. Evaporation by evaporator 4 forms low-temperature, low-pressure gas, which is then transported 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 mounted to the second axial end of the rotating shaft 10. The motor 70 is mounted on the rotating shaft 10, located between the impeller 20 and the end cover 60. The housing 100 covers the motor 70. Two bearing blocks 80 are respectively disposed at the axial ends of the motor 70 and connected to the housing 100. Two bearings 90 are respectively mounted in the two bearing blocks 80. The rotating shaft 10 is rotatably supported by the two bearing blocks 80 via 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 serving 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 open at the axial second end of the rotating shaft 10. The opening at the axial second end forms a rotating shaft inlet 12. The diameter of the center hole is 1 / 8~1 / 10, for example 1 / 9, of the maximum diameter of the rotating shaft 10. The hole wall of the center hole is provided with a plurality of protrusions (not shown) as a spoiler structure. The axial second end of the center hole includes a necked-down section 111 provided at the rotating shaft inlet 12. The necked-down section 111 gradually decreases the flow area from the rotating shaft inlet 12 to the side away from the rotating shaft inlet 12.

[0086] As shown in FIGS. 1, 2 and 3, a plurality of rotating shaft outlets 13 are provided corresponding to the plurality of rotating shaft inlets 12 and are uniformly distributed along the circumference of the rotating shaft 10. Each rotating shaft outlet 13 is connected to a corresponding rotating shaft inlet 12. The rotating shaft outlet 13 is inclined from the hollow portion 11 to the rotating shaft inlet 12 in the direction from the axial second end of the rotating shaft to the axial first end of the rotating shaft. The angle β between the rotating shaft outlet 13 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. Figure 2 Figure 3 As shown in FIGS. 1, 2 and 3, a plurality of rotating shaft outlets 13 are provided corresponding to the plurality of rotating shaft inlets 12 and are uniformly distributed along the circumference of the rotating shaft 10. Each rotating shaft outlet 13 is connected to a corresponding rotating shaft inlet 12. The rotating shaft outlet 13 is inclined from the hollow portion 11 to the rotating shaft inlet 12 in the direction from the axial second end of the rotating shaft to the axial first end of the rotating shaft. The angle β between the rotating shaft outlet 13 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 rotating shaft outlets 13 and the plurality of communication holes 14 is equal to the number of the 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 center 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 center hole.

[0088] The diffuser 30 is located radially outward of the impeller 20. The diffuser 30 includes two opposite diffuser end walls, and a diffuser flow passage 34 is formed between the two diffuser end walls. The radially inner side of the diffuser flow passage 34 forms a diffuser inlet 32 opposite the impeller outlet. The radially outer side of the diffuser flow passage 34 forms a diffuser outlet 33. The noise reduction gas inlet 35 is an annular port coaxial with the impeller 20, formed on the diffuser end wall 31 on the side away from the axial first end of the impeller 20 and radially close to the diffuser inlet 32 of the impeller 20.

[0089] The oil blocking sleeve 40 is located radially inward 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 spacing 50 with the end face of the axial second end of the impeller 20. The spacing 50 is respectively communicated with the plurality of rotating shaft outlets 13 and the noise reduction fluid inlet 35. The noise reduction fluid inlet 35 receives the noise reduction fluid through the spacing 50. The plurality of rotating shaft outlets 13 are opposite to the radially inner side of the spacing forming the spacing 50.

[0090] ​The end cover 60 is rotatably covered on the shaft 10 at the shaft inlet 12. The end cover 60 is provided with a port 63 communicating with the shaft inlet 12. A comb seal structure is provided between the end cover 60 and the shaft 10 as a sealing structure 64. The comb seal structure can prevent the noise reduction fluid from leaking while not affecting the rotation of the shaft 10.

[0091] The end cover 60 includes an end cover end wall 61 and a side wall 62 connected to the outer periphery of the end cover end wall 61. The port 63 is arranged at the radial middle of the end cover end wall 61. The side wall 62 is sleeved on the axial second end of the shaft 10. The comb seal structure is arranged on the radial inner side of the side wall 62. The end cover end wall 61 is spaced from the end face of the axial second end of the shaft 10, so that the buffer cavity C is formed between the end cover 60 and the shaft 10 to communicate the port 63 and the shaft inlet 12.

[0092] In the air conditioning unit of the embodiment of the present application, the shaft 10 of the compressor 1 has a central hole. The high-pressure liquid refrigerant as the noise reduction fluid can be introduced into the shaft inlet 12 of the axial second end of the shaft 10 from the condenser through the conduit 9 connected to the port 63 of the end cover 60, and then the noise reduction fluid flows through the central hole as the hollow part 11, the plurality of communication holes 14, the plurality of shaft outlets 13 and enters the interval 50, and under the rotation of the shaft 10 and the impeller 20, the noise reduction fluid enters the diffuser inlet 32 of the diffuser passage 34 from the noise reduction fluid inlet 35 arranged on the end plate 31 at the radial outer end of the oil blocking sleeve 40 by the centrifugal force, the pressure of the noise reduction fluid itself and the suction force of the high-pressure exhaust gas of the impeller outlet 23 of the impeller 20. On the one hand, the flow of high-pressure liquid refrigerant in the central hole of the shaft 10 can take away the heat generated by the shaft 10 during operation, thereby ensuring the stability of the operation of the compressor 1. On the other hand, the high-pressure liquid refrigerant encounters the high-temperature exhaust gas of the impeller outlet 23 to form a misty fluid, and the misty 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 noise of the operation of the compressor 1. The flow direction of the refrigerant in the compressor is shown in Figure 1 and Figure 2 Therefore, the compressor and the air conditioning unit of the embodiment of the present application can reduce the noise of the operation of the compressor while reducing the temperature of the shaft of the compressor, and do not 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 solutions of the present application and not to limit them; although the present application has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the specific embodiments of the present application can be modified or some technical features can be replaced by equivalent replacements, which should be covered in the technical solution range claimed by the present application.

Claims

1. A compressor, characterized in that: include: Rotating shaft (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) includes a diffuser end wall (31) located at an end away from the impeller inlet (22) along the axial direction of the impeller (20), and the noise reduction fluid inlet (35) is provided on the diffuser 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 diffuser 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) has a hollow portion (11), a rotating shaft inlet (12) for conveying the noise reduction fluid to 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 provided 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 provided 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), and 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 two or more rotating shaft outlets (13) arranged along the circumference of the rotating shaft (10) and two or more communicating holes (14) corresponding one-to-one to the two or more 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 gap (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 of the rotating shaft (10), and / or the sum of the flow areas of the two or more communicating holes (14) is equal to the sum of the flow areas of the central hole of the rotating shaft (10).

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 communicating 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 rotatable relative to each other and being 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 cover end wall (61) and a side wall (62) connected to the outer periphery of the end cover end wall (61); the port (63) is arranged on the end cover 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).

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