Compressor and refrigeration equipment

Abstract

The utility model provides a compressor and refrigeration equipment. A compressor is provided with: a housing (1) having an intake port (13) and an exhaust port (14); and the rotor (2) is rotatably arranged in the shell (1) so as to compress air entering from the air suction port (13) and enable the compressed air to be exhausted from the air exhaust port (14), a cooling hole (3) is formed in the rotor (2), and the cooling hole (3) guides a cooling medium to flow in the rotor (2) so as to cool the rotor (2). Therefore, the performance of the compressor can be improved.

Description

Technical Field

[0001] The present application relates to the field of refrigeration technology, and in particular to a compressor and refrigeration equipment. Background Art

[0002] The compressor is an important component of refrigeration equipment such as air conditioners and refrigerators. It compresses the gas through the rotation of the rotor.

[0003] During the operation of the compressor, a large amount of heat is generated, causing the rotor to expand due to heat, triggering mechanical friction, locking or leakage, causing damage to the compressor structure, shutdown or reduced efficiency, and affecting the performance of the compressor. Utility Model Content

[0004] A technical problem to be solved by this application is to improve the performance of the compressor.

[0005] In order to solve the above technical problems, the present application provides a compressor, comprising:

[0006] a housing having an air intake and an air exhaust; and

[0007] The rotor is rotatably disposed in the housing to compress the gas entering from the intake port and discharge the compressed gas from the exhaust port. Cooling holes are provided inside the rotor to guide the cooling medium to flow inside the rotor to cool the rotor.

[0008] In some embodiments, the compressor is configured as at least one of the following:

[0009] The cooling holes are offset from the central axis of the rotor;

[0010] A guide groove is provided on the axial end surface of the rotor, which is connected to the cooling hole and guides the cooling medium to flow to the cooling hole;

[0011] A storage chamber is provided between the rotor and the housing. The storage chamber is in communication with the cooling holes to receive the cooling medium flowing out of the cooling holes. A sealing structure is provided between the rotor and the housing to seal the storage chamber so that the cooling medium in the storage chamber exerts a force on the rotor in a direction from the air intake to the air discharge port.

[0012] At least two cooling holes are provided inside the rotor;

[0013] The diameter of the cooling hole is 3~12mm;

[0014] The housing is also provided with a nozzle, which is used to guide the cooling medium to the outer surface of the rotor to cool the rotor;

[0015] The cooling medium includes lubricating oil.

[0016] In some embodiments, at least two cooling holes are provided inside the rotor, and the at least two cooling holes are spaced apart along the circumference of the rotor.

[0017] In some embodiments, the rotor is provided with at least two teeth distributed along the circumferential direction, and in the circumferential direction of the rotor, at least two cooling holes correspond one-to-one to the at least two teeth distributed along the circumferential direction.

[0018] In some embodiments, on the exhaust end face of the rotor, each cooling hole is located directly below the tooth top of the corresponding tooth. The exhaust end face of the rotor is the axial end face of the rotor facing the exhaust port and having an axial clearance fit with the housing.

[0019] In some embodiments, the drainage channel is configured as at least one of the following:

[0020] The drainage trough is annular;

[0021] The width of the drainage groove is greater than or equal to the diameter of the cooling hole;

[0022] The depth of the drainage groove is 0.8~1.2 times the diameter of the cooling hole;

[0023] The distance between the outer edge of the drainage groove and the tooth root of the teeth on the rotor in the radial direction of the rotor is greater than or equal to L, and L is 3-5 mm.

[0024] In some embodiments, at least two cooling holes are provided in the annular drainage groove and are spaced apart along the circumferential direction.

[0025] In some embodiments, the axial end face of the rotor provided with the drainage groove is the exhaust end face of the rotor, and the exhaust end face of the rotor is the axial end face of the rotor facing the exhaust port and having an axial clearance fit with the housing.

[0026] In some embodiments, the storage cavity is connected to the outside of the storage cavity so that the cooling medium flowing from the cooling hole into the storage cavity flows to the outside of the storage cavity; and / or, the sealing structure includes at least one of a comb tooth seal, a graphite ring seal and a lip seal.

[0027] In some embodiments, the storage chamber is communicated with the outside of the storage chamber through a sealing structure; or, at least one of the housing and the rotor is provided with a leakage hole, and the storage chamber is communicated with the outside of the storage chamber through the leakage hole.

[0028] In some embodiments, the sealing structure includes a comb seal portion, and the comb seal portion is configured as at least one of the following:

[0029] The comb seal is located between the axial end surface of the rotor and the housing;

[0030] The comb seal is located between the circumferential surface of the rotor and the housing;

[0031] The number of teeth on the comb seal is 3 to 5;

[0032] The gap between the tooth tip of the comb seal and the rotor is 5% to 15% of the cooling hole diameter.

[0033] In some embodiments, the sealing structure includes a graphite ring seal located between the axial end surface of the rotor and the housing; and / or the sealing structure includes a lip seal located between the circumferential surface of the rotor and the housing.

[0034] In some embodiments, the storage chamber is located on a side of the rotor's suction end face away from the exhaust port. The rotor's suction end face is the axial end face of the rotor facing the suction port and having an axial clearance fit with the housing.

[0035] In some embodiments, the cooling hole is configured as at least one of the following:

[0036] At least part of the cooling hole extends in the axial direction and / or radial direction of the rotor;

[0037] The cooling hole passes through the exhaust end face of the rotor, and the exhaust end face of the rotor is the axial end face of the rotor facing the exhaust port and having an axial clearance fit with the housing;

[0038] The cooling hole passes through the suction end face of the rotor. The suction end face of the rotor is the axial end face of the rotor facing the suction port and having an axial clearance fit with the shell.

[0039] In some embodiments, the cooling holes extend along the axial direction of the rotor; and / or the cooling medium flows into the cooling holes from the exhaust end face; and / or the cooling medium flows out of the cooling holes from the intake end face.

[0040] In addition, the present application also provides a refrigeration device, which includes the compressor of any embodiment.

[0041] By setting cooling holes inside the rotor to guide the flow of cooling medium, the rotor can be cooled, which can effectively reduce the thermal expansion of the rotor during the operation of the compressor, improve the structure and working reliability of the compressor, and improve the efficiency of the compressor, thereby effectively improving the performance of the compressor.

[0042] 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

[0043] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0044] Figure 1 This is a simplified structural diagram of the compressor in some embodiments of the present application.

[0045] Figure 2 for Figure 1 Schematic diagram of the middle rotor.

[0046] Figure 3 for Figure 2 main view.

[0047] Figure 4 for Figure 2 sectional view of .

[0048] Figure 5 for Figure 1 A local enlarged schematic diagram at point I.

[0049] Figure 6 This is a partially enlarged schematic diagram of the compressor at position I in some other embodiments of the present application.

[0050] Figure 7 Schematic diagram of the rotor before and after thermal expansion.

[0051] Description of reference numerals:

[0052] 10. Compressor;

[0053] 1. Housing; 11. Shell; 12. Support portion; 13. Air inlet; 14. Air outlet; 15. Inlet; 16. Nozzle; 17. First end surface; 18. Second end surface;

[0054] 2. Rotor; 21. Support section; 22. Working section; 23. Tooth; 24. Tooth top; 25. Tooth root; 26. Exhaust end face; 27. Intake end face;

[0055] 3. Cooling holes;

[0056] 4. Drainage trough;

[0057] 5. Storage cavity;

[0058] 6. Sealing structure; 61. Comb seal; 62. Graphite ring seal; 63. Lip seal;

[0059] 7. Leakage hole;

[0060] 8. Bearings. DETAILED DESCRIPTION

[0061] 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, not all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is in no way 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 carrying out creative work are within the scope of protection of this application.

[0062] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered part of the specification.

[0063] In the description of this application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "horizontal, vertical, vertical, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction. Therefore, they cannot be understood as limiting the scope of protection of this application; the directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0064] In the description of this application, it should be understood that the use of words such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above words have no special meaning and therefore cannot be understood as limiting the scope of protection of this application.

[0065] 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.

[0066] In order to improve the performance of the compressor, the present application provides a compressor and a refrigeration device, which mainly reduces the thermal expansion of the compressor rotor by improving the structure of the compressor, thereby improving the performance of the compressor.

[0067] Figures 1-6 The structure of the compressor in this application is shown as an example.

[0068] See also Figures 1-6In the present application, a compressor 10 includes a housing 1 and a rotor 2. The housing 1 has an intake port 13 and an exhaust port 14 for compressed gas to enter and exit, respectively. The rotor 2 is rotatably disposed within the housing 1 to compress the gas entering through the intake port 13 and discharge the compressed gas through the exhaust port 14.

[0069] The rotor 2 has an exhaust end face 26 and an intake end face 27. The exhaust end face 26 and the intake end face 27 are both axial end faces of the rotor 2 used for axial clearance fit with the housing 1. The two are arranged in sequence along the direction from the exhaust port 14 to the intake port 13, close to and away from the exhaust port 14 respectively. Among them, the exhaust end face 26 is the axial end face of the rotor 2 facing the exhaust port 14 and having an axial clearance fit with the housing 1. The intake end face 27 is the axial end face of the rotor 2 facing the intake port 13 and having an axial clearance fit with the housing 1. The portion of the housing 1 used for axial clearance fit with the exhaust end face 26 and the intake end face 27 is located at Figure 1 The first end face 17 and the second end face 18 are respectively marked in the figure. The first end face 17 and the second end face 18 are both internal axial end faces of the housing 1, located inside the housing 1, and arranged in sequence along the direction from the exhaust port 14 to the intake port 13. The first end face 17 is close to the exhaust port 14 and faces the intake port 13. The second end face 18 is close to the intake port 13 and faces the exhaust port 14. The exhaust end face 26 and the first end face 17 are opposite to each other and have a clearance fit. The corresponding gap can be called the exhaust end gap. The intake end face 27 and the second end face 18 are opposite to each other and have a clearance fit. The corresponding gap can be called the intake end gap.

[0070] Specifically, see Figure 1 In some embodiments, the rotor 2 is provided with teeth 23. These teeth 23 protrude radially outward and cooperate with the teeth 23 of another rotor 2 (e.g., the other rotor 2 in a twin-rotor compressor) or the housing 1 to form a chamber with a variable volume. This allows gas to be compressed by the volume change at the teeth 23 during the rotation of the rotor 2. In this case, the exhaust end face 26 and the intake end face 27 are typically the axial end faces of the portion of the rotor 2 provided with the teeth 23.

[0071] More specifically, see Figures 1-4 In some embodiments, the rotor 2 includes a working section 22 and two supporting sections 21. Teeth 23 are provided on the working section 22. Typically, the working section 22 is provided with at least two (e.g., multiple, i.e., at least three) teeth 23 along the circumferential direction, so that the rotor 2 includes at least two teeth 23 arranged along the circumferential direction. The two supporting sections 21 are connected to the axial ends of the working section 22 and are respectively supported on the housing 1 by bearings 8, so that the rotor 2 is rotatably provided as a whole in the housing 1. Typically, of the two supporting sections 21, the supporting section 21 located on the exhaust port 14 side is axially fixed at the bearing 8.

[0072] The diameters of the two support segments 21 are smaller than the diameter of the working segment 22, so that the connection between the working segment 22 and the two support segments 21 forms an axial end face, which is clearance-matched with the first end face 17 and the second end face 18, respectively, to form an exhaust end face 26 and an intake end face 27. In this case, the exhaust end face 26 is the axial end face of the working segment 22 that is close to the exhaust port 14 and is also the axial end face of the rotor 2 that is provided with the teeth 23 and is closest to the exhaust port 14. The intake end face 27 is the axial end face of the working segment 22 that is farthest from the exhaust port 14 and is also the axial end face of the rotor 2 that is provided with the teeth 23 and is farthest from the exhaust port 14.

[0073] The exhaust end clearance, the intake end clearance, and the tooth top clearance (i.e., the clearance between the tooth top 24 of the tooth 23 and the teeth 23 of other rotors 2 or the housing 1) are important indicators that affect the performance of the compressor 10. All three should be neither too large nor too small. Otherwise, if they are too large, the fluid in the compressor 10 will leak, affecting the compression efficiency. If they are too small, they are prone to friction or even locking, causing structural damage or even shutdown.

[0074] During the operation of the compressor 10, a large amount of heat is generated, causing the rotor 2, especially the side of the rotor 2 near the exhaust port 14 (referred to as the exhaust side), to increase in temperature. When the rotor 2 heats up, it will expand due to the heat, and the higher the temperature, the greater the expansion. The thermal expansion of the rotor can easily cause mechanical friction, locking, and fluid leakage in the compressor 10. For example, see Figure 7 When the rotor 2 is heated, it will expand radially. Figure 7 The position indicated by the solid line expands to the position indicated by the dotted line. If the radial expansion of the rotor 2 is large, it may cause mechanical friction with the inner wall of the housing 1, and even cause the rotor to lock, resulting in structural damage and shutdown problems. For another example, see Figure 7 , the rotor will expand axially after being heated, and since the rotor 2 is axially fixed at the bearing 8 on the exhaust side, see Figure 7 As shown by the dotted line in the figure, after the rotor expands due to heat, its exhaust end surface 26 will move to the side away from the exhaust port 14, causing the exhaust end gap to become larger. If the rotor 2 expands axially to a large extent, the exhaust end gap will be too large, causing fluid leakage in the compressor 10, affecting the efficiency of the compressor 10.

[0075] It can be seen that the rotor 2 of the compressor 10 is easily heated and expanded during the operation of the compressor 10, causing mechanical friction, locking or leakage, resulting in damage to the compressor structure, shutdown or reduced efficiency, and affecting the performance of the compressor.

[0076] In view of the above situation, in order to reduce the thermal expansion of the rotor 2 and improve the performance of the compressor 10, see Figures 1-6In the present application, cooling holes 3 are provided inside the rotor 2 of the compressor 10 , and the cooling holes 3 guide the cooling medium to flow inside the rotor 2 to cool the rotor 2 .

[0077] By providing cooling holes 3 and introducing the cooling medium to the rotor 2, the rotor 2 is cooled, which can effectively reduce the temperature of the rotor 2 during the operation of the compressor 10, reduce the thermal expansion of the rotor 2 during the operation of the compressor 10, and thereby reduce the risk of mechanical friction, locking or leakage caused by the thermal expansion of the rotor 2, so as to avoid mechanical friction, locking or leakage at the rotor 2, which may cause damage to the compressor structure, shutdown or reduced efficiency. In this way, the structure and working reliability of the compressor 10 can be effectively improved, the efficiency of the compressor 10 can be improved, and therefore the performance of the compressor 10 can be effectively improved.

[0078] In particular, since the cooling holes 3 are provided within the rotor 2, the cooling medium can be directed to flow within the rotor 2, thereby cooling the rotor 2 from within the rotor 2. Compared to a method of cooling the outer surface of the rotor 2 by spraying the cooling medium onto the outer surface of the rotor 2, the rotor 2 can be cooled more fully and a better cooling effect can be achieved. Therefore, it is more conducive to reducing the thermal expansion of the rotor 2 during the operation of the compressor 10, thereby more effectively improving the performance of the compressor 10. Of course, while providing the cooling holes 3 within the rotor 2, a nozzle 16 can also be provided on the housing 1 to direct the cooling medium toward the outer surface of the rotor 2 to cool the rotor 2. In this case, the rotor 2 is cooled not only by allowing the cooling medium to flow within the rotor 2, but also by spraying the cooling medium onto the outer surface of the rotor 2, thereby achieving a cooling method that combines internal and external cooling. This cooling method that combines internal and external cooling can achieve a better cooling effect, thereby more conducive to reducing the thermal expansion of the rotor 2 during the operation of the compressor 10, thereby more effectively improving the performance of the compressor 10.

[0079] It can be seen that by setting cooling holes 3 inside the rotor 2 to guide the flow of cooling medium, the rotor 2 is cooled, which can effectively reduce the thermal expansion of the rotor 2 during the operation of the compressor 10, improve the structure and working reliability of the compressor 10, and improve the efficiency of the compressor 10, thereby effectively improving the performance of the compressor 10.

[0080] In the present application, the cooling medium can be any fluid (such as gas or liquid) that can cool the rotor 2. As an example, in some embodiments, the cooling medium includes the same low-temperature compressed medium as in the compressor 10; in other embodiments, the cooling medium includes oil such as lubricating oil. Since the compressor 10 usually needs to be lubricated with lubricating oil, the lubricating oil is easy to obtain nearby, and compared with other cooling media, the lubricating oil temperature is more controllable and easier to seal, and is less likely to leak under the same gap. At the same time, it can also play a lubricating role. Therefore, when the cooling medium includes lubricating oil, it is more conducive to simplifying the structure, reducing costs, and improving the cooling effect. It is convenient to achieve better cooling effects based on a simpler structure and lower costs, more effectively reduce the thermal expansion of the rotor 2 during the operation of the compressor 10, and improve the performance of the compressor 10.

[0081] In addition, in the present application, the cooling holes 3 can be arranged in various ways.

[0082] For example, the number of cooling holes 3 is not limited and can be one or at least two (i.e., two or at least three). Compared to a case where only one cooling hole 3 is provided, when at least two cooling holes 3 are provided within the rotor 2, due to the greater number of cooling holes 3, the cooling medium can be directed to flow through more areas within the rotor 2, cooling more parts of the rotor 2. Therefore, the cooling effect is better, the thermal expansion of the rotor 2 can be further reduced, and the performance of the compressor 10 can be more effectively improved.

[0083] For another example, the extension direction of the cooling hole 3 is not limited and can be along the axial direction and / or radial direction of the rotor 2. As an example, at least a portion of the cooling hole 3 extends along the axial direction and / or radial direction of the rotor 2, so that the cooling medium can flow along the axial direction and / or radial direction of the rotor 2 inside the rotor 2, effectively cooling the rotor 2. Compared with the case of extending in the radial direction, when the cooling hole 3 extends in the axial direction, it is not restricted by the teeth 23 and is not easy to damage the teeth 23. Therefore, it is more convenient to set it up. Moreover, since the cooling hole 3 extending in the axial direction can guide the cooling medium to flow in the rotor 2 along the axial direction of the rotor 2, it is convenient to effectively cool both the exhaust side and the intake side, so it can also achieve a better cooling effect. It can be seen that constructing the cooling hole 3 to extend in the axial direction of the rotor 2 is convenient for achieving a better cooling effect based on a simpler structure and more effectively improving the performance of the compressor 10.

[0084] Among them, when the cooling hole 3 extends along the axial direction, the cooling medium in the cooling hole 3 can flow in the direction from the exhaust port 14 to the intake port 13, or can flow in the direction from the intake port 13 to the exhaust port 14. Compared with the case where the cooling medium flows in the direction from the intake port 13 to the exhaust port, when the cooling medium flows in the direction from the exhaust port 14 to the intake port 13, the cooling medium can flow through the exhaust side with a higher temperature and the intake side with a lower temperature in sequence. Since the cooling medium temperature is relatively low when flowing through the exhaust side, it can more effectively cool the exhaust side with a higher temperature. Moreover, although the cooling medium temperature rises when flowing through the intake side, the intake side has a lower temperature and a lower cooling demand. Therefore, the cooling medium can still well meet the cooling demand of the intake side and effectively cool the intake side. It can be seen that in this case, the flow of the cooling medium is more in line with the changing trend of the cooling demand of the rotor, and can achieve a better cooling effect.

[0085] For another example, the position of the cooling hole 3 is not limited and can be located at or not at the center of the rotor 2. When the cooling hole 3 is not located at the center of the rotor 2, the cooling hole 3 deviates from the central axis of the rotor 2 and is closer to the outer surface of the rotor 2. In this case, the cooling medium flowing through the cooling hole 3 can better meet the cooling requirements of the center and outer surface of the rotor 2. While effectively cooling the interior of the rotor 2, it also cools the outer surface of the rotor 2. In this way, the cooling effect of the rotor 2 can be further improved, the thermal expansion of the rotor 2 can be further reduced, and the performance of the compressor 10 can be improved. The corresponding effect is more prominent when the teeth 23 are provided on the rotor 2, because, see Figures 1-4 When teeth 23 are provided on the rotor 2, the radial dimension of the rotor 2 at the teeth 23 is the largest, and in particular, the thickness at the tooth top 24 of the tooth 23 is the largest. Regardless of whether external spraying of cooling medium is adopted or cooling holes 3 are provided in the center of the rotor 2, it is difficult to effectively cool the teeth 23, especially the tooth top 24 of the tooth 23, and the cooling effect is poor. For example, if cooling holes 3 are provided only in the center of the rotor 2, then under the same diameter conditions, the cooling holes 3 are far away from the teeth 23, and the cooling medium flowing through the cooling holes 3 is difficult to effectively cool the teeth 23, especially the tooth top 24 of the teeth 23, and the cooling effect is poor. If the cooling holes 3 are deviated from the central axis of the rotor 2, the cooling holes 3 are closer to the teeth 23, and can more effectively cool the teeth 23, especially the tooth top 24, thereby facilitating a more sufficient cooling effect, thereby further reducing the thermal expansion of the rotor 2 and improving the performance of the compressor 10.

[0086] The number of the cooling holes 3 deviating from the central axis of the rotor 2 may also be one or at least two.

[0087] For example, see Figure 2-Figure 3In some embodiments, at least two cooling holes 3 are provided inside the rotor 2, and these at least two cooling holes 3 are arranged at intervals along the circumference of the rotor 2. Based on this, the rotor 2 is provided with not only one cooling hole 3, but two or more cooling holes 3, and the number of cooling holes 3 is greater. Moreover, each cooling hole 3 is not located at the center of the rotor 2, but is offset from the center of the rotor 2 and located radially outward from the center of the rotor 2, closer to the outer surface of the rotor 2. The cooling medium flowing through the cooling holes 3 can not only effectively cool the inside of the rotor 2, but also has a certain cooling effect on the outer surface of the rotor 2. Therefore, the cooling effect of the rotor 2 can be further improved, the thermal expansion of the rotor 2 can be more effectively reduced, and the performance of the compressor 10 can be improved. The corresponding effect is more prominent when the teeth 23 are provided on the rotor 2.

[0088] It can be seen that by providing at least two cooling holes 3 arranged circumferentially spaced apart inside the rotor 2, the rotor 2 can be cooled more fully, especially the rotor 2 having teeth 23. Therefore, it is more conducive to reducing the thermal expansion of the rotor 2 and improving the performance of the compressor 10.

[0089] Furthermore, in order to achieve better cooling of the rotor 2 provided with the teeth 23, see Figure 1-Figure 3 In some embodiments, at least two cooling holes 3 of the rotor 2 correspond to at least two circumferentially distributed teeth 23 of the rotor 2 in a one-to-one manner. Thus, each tooth 23 is provided with a corresponding cooling hole 3 in the circumferential direction of the rotor 2. The cooling medium flowing through each cooling hole 3 can fully cool the corresponding tooth 23, thereby facilitating better cooling of the rotor 2 provided with the teeth 23, thereby more effectively reducing thermal expansion of the rotor 2 and improving the performance of the compressor 10.

[0090] Further, see Figure 2 and Figure 3 In some embodiments, on the exhaust end surface 26 of the rotor 2 , the cooling hole 3 is located directly below the tooth top 24 of the corresponding tooth 23 .

[0091] As mentioned above, for the rotor 2 provided with teeth 23, the thickness is the largest at the tooth top 24 of the tooth 23, and the cooling difficulty is the greatest. Constructing the cooling hole 3 to be located directly below the tooth top 24 of the corresponding tooth 23 on the exhaust end face 26 is conducive to more fully exerting the cooling effect of the cooling medium in the cooling hole 3 and more fully cooling the tooth top 24 with the largest thickness. Therefore, it is more conducive to reducing the thermal expansion of the rotor 2 and improving the performance of the compressor 10.

[0092] It should be noted that the cooling hole 3 is located directly below the tooth top 24 of the corresponding tooth 23, which means that the cooling hole 3 is approximately located directly below the tooth top 24 of the corresponding tooth 23, including the situation that the cooling hole 3 is exactly located directly below the tooth top 24 of the corresponding tooth 23, and also includes the situation that although it is not exactly located directly below the tooth top 24 of the corresponding tooth 23, there is a deviation between the two in the circumferential direction, but the deviation is small and within the allowable range. In addition, when the rotor 2 is provided with teeth 23, the exhaust end face 26 of the rotor 2 can be regarded as the starting end face of the tooth 23. In the direction from the corresponding exhaust end face 26 toward the exhaust port 14, that is, in the direction from the exhaust end face 26 to the intake end face 27 of the rotor 2, the tooth 23 gradually twists. Therefore, the cooling hole 3 is located directly below the tooth top 24 of the corresponding tooth 23 on the exhaust end face 26 of the rotor 2, which means that the cooling hole 3 may not be located directly below the tooth top 24 of the corresponding tooth 23 on other cross-sections of the rotor 2 such as the intake end face 27 where the teeth 23 are provided, but deviate from the tooth top 24 of the corresponding tooth 23. However, considering that the temperature is lower the closer to the intake side, this deviation is acceptable.

[0093] In the aforementioned embodiments, the diameter of the cooling hole 3 can be 3 to 12 mm, for example, 4, 6, 7, 9, 10, or 11 mm. In this case, the diameter of the cooling hole 3 is relatively suitable, which is convenient for processing and can effectively meet the flow rate requirements of the cooling medium in most cases, thereby achieving a good cooling effect.

[0094] Also, see Figures 1-6 The cooling hole 3 in the aforementioned embodiments may penetrate at least one of the exhaust end face 26 and the intake end face 27 .

[0095] The cooling hole 3 passes through at least one of the exhaust end face 26 and the intake end face 27 of the rotor 2, which means that the cooling hole 3 is provided with an inlet or an outlet on at least one of the exhaust end face 26 and the intake end face 27 of the rotor 2, and the cooling medium can flow into or out of the cooling hole 3 from at least one of the exhaust end face 26 and the intake end face 27. This facilitates and more effectively improves the performance of the compressor 10, because when the cooling medium flows into or out of at least one of the exhaust end face 26 and the intake end face 27, it can also play a certain cooling role on at least one of the exhaust end face 26 and the intake end face 27, thereby achieving more sufficient cooling of the rotor 2 and more effectively reducing the thermal expansion of the rotor 2. Moreover, the cooling medium, especially the cooling medium including oil such as lubricating oil, can also achieve fluid sealing on at least one of the exhaust end face 26 and the intake end face 27, further reducing leakage, all of which are conducive to further improving the performance of the compressor 10.

[0096] As mentioned above, the end face of the rotor 2 provided with the teeth 23 and closest to the exhaust port 14 is located between the two axial ends of the rotor 2, and is the exhaust end face of the rotor 2. It is the part of the rotor 2 with the highest temperature rise, the most obvious thermal expansion, and the most prone to leakage. Therefore, when the cooling hole 3 passes through the exhaust end face 26, it means that the cooling medium can flow into or out of the cooling hole 3 from the exhaust end face, and cool and oil-seal the exhaust end face with the highest temperature rise, the most obvious thermal expansion, and the most prone to leakage. This is conducive to further reducing the risks of mechanical friction, locking and leakage, and more effectively improving the performance of the compressor 10.

[0097] In addition, as mentioned above, the amount of thermal expansion of the suction end face 27 of the rotor 2 affects the size of the suction end face gap, which is also a relatively important structural feature of the rotor 2. Therefore, when the cooling hole 3 passes through the suction end face 27, and the suction end face 27 is the end face of the rotor 2 with teeth 23 and farthest from the exhaust port 14, it means that the cooling medium can flow into or out of the cooling hole 3 from the suction end face, cooling and oil sealing the corresponding suction end face, which is conducive to further reducing the risks of mechanical friction, locking and leakage, and more effectively improving the performance of the compressor 10.

[0098] It can be seen that configuring the cooling hole 3 to penetrate at least one of the exhaust end surface 26 and the intake end surface 27 of the rotor 2 is beneficial to further improve the performance of the compressor 10 .

[0099] When the cooling hole 3 passes through the exhaust end face 26 , the cooling medium can flow into or out of the cooling hole 3 from the exhaust end face 26 . When the cooling hole 3 passes through the intake end face 27 , the cooling medium can flow into or out of the cooling hole 3 from the intake end face 27 .

[0100] Among them, when the cooling hole 3 passes through the exhaust end face 26 and the cooling medium flows into the cooling hole 3 from the exhaust end face 26, the cooling medium can first flow through the exhaust side with a higher temperature. At this time, the cooling medium temperature is lower, and the exhaust end face 26 and other parts of the rotor 2 located on the exhaust side with a higher temperature can be cooled more fully, achieving a better cooling effect, and therefore, being more conducive to improving the performance of the compressor 10.

[0101] When the cooling hole 3 passes through the intake end face 27 and the cooling medium flows out of the cooling hole 3 from the intake end face 27, since the cooling medium is discharged from the intake side, it is convenient to use the cooling medium to establish a force F2 in the opposite direction to the gas force F1 exerted by the compressed gas on the rotor 2, and use the cooling medium to balance the gas force F1 exerted by the compressed gas on the rotor 2. In this way, the load on the bearing 8 can be reduced, the reliability of the bearing 8 and the compressor 10 can be improved, and the service life of the bearing 8 and the compressor 10 can be extended.

[0102] The compressed gas is gradually compressed along the direction from the air inlet 13 to the air outlet 14, and the pressure gradually increases. In this process, the compressed gas is subjected to the force exerted by the rotor 2 toward the air outlet 14. According to the mutuality of forces, the gas also exerts a force on the rotor 2 toward the air inlet 13. The force exerted by the gas on the rotor 2 toward the air inlet 13 is called the gas force F1. Figure 1 As shown, the gas force F1 is along the direction from the exhaust port 14 to the intake port 13. The corresponding gas force F1 is mainly borne by the bearing 8 supporting the rotor 2. The greater the gas force F1 borne by the bearing 8, the easier it is to be damaged, affecting the reliability and life of the bearing 8 and the compressor 10.

[0103] In the related art, a balancing piston is typically provided on the suction side. The balancing piston uses high-pressure fluid to apply a force opposite to the gas force F1 to the rotor 2, thereby balancing the gas force F1 and reducing the load on the bearing 8. However, this method of using a balancing piston to balance the gas force F1 requires specialized piping and drive cylinders, resulting in a relatively complex structure.

[0104] The cooling medium is used to create a force F2 in the opposite direction to the gas force F1 exerted by the compressed gas on the rotor 2 to balance the gas force F1. Since there is no need to configure special pipelines and drive cylinders and other components, the structure is relatively simple.

[0105] It can be seen that using the cooling medium to balance the gas force F1 can reduce the bearing load based on a simpler structure, improve the reliability of the bearing 8 and the compressor 10, and extend the service life of the bearing 8 and the compressor 10.

[0106] To balance the gas forces with a cooling medium, see Figure 1 as well as Figure 5 and Figure 6 In some embodiments, a storage chamber 5 is provided between the rotor 2 and the housing 1. The storage chamber 5 is communicated with the cooling hole 3 to receive the cooling medium flowing out of the cooling hole 3. In addition, a sealing structure 6 is provided between the rotor 2 and the housing 1. The sealing structure 6 seals the storage chamber 5 so that the cooling medium in the storage chamber 5 applies a force to the rotor 2 in the direction from the intake port 13 to the exhaust port 14 (i.e., toward the exhaust port 14).

[0107] The use of the sealing structure 6 to seal the storage chamber 5 for receiving the flow from the cooling hole 3 can cause the cooling medium flowing out of the cooling hole 3 to establish a high pressure in the storage chamber 5, exerting a force F2 on the rotor 2 toward the exhaust side. Since the corresponding force F2 is in the opposite direction of the gas force F1, it can offset a portion of the gas force F1, thereby balancing the gas force. Therefore, it can effectively reduce the load on the bearing 8, improve the reliability of the bearing 8 and the compressor 10, and extend the life of the bearing 8 and the compressor 10. In addition, the use of the sealing structure 6 to seal the storage chamber 5 can also prevent the cooling medium on the inlet side of the cooling hole 3 from overflowing, forming a fluid seal and effectively reducing the gap value. For example, when the inlet of the cooling hole 3 is located on the exhaust end face 26, the cooling medium can fill the gap between the exhaust end faces, forming a seal and reducing the gap between the exhaust end faces. This helps to reduce leakage and improve efficiency.

[0108] The position of the storage chamber 5 can be varied, as long as the cooling medium sealed by the sealing structure 6 can exert a force on the rotor 2 toward the exhaust port 14. As one of them, see Figure 1 as well as Figure 5 and Figure 6 In some embodiments, the storage chamber 5 is located on the side of the intake end face 27 of the rotor 2 that is away from the exhaust port 14. Since the intake end face 27 is located on the intake side, providing the storage chamber 5 on the side of the intake end face 27 that is away from the exhaust port 14 can conveniently cause the cooling medium in the storage chamber 5 to exert a force on the rotor 2 toward the exhaust port 14, thereby achieving a gas force balancing function.

[0109] It can be understood that although the storage chamber 5 is sealed with a sealing structure 6, the storage chamber 5 is not disconnected from the outside, and the cooling medium in the storage chamber 5 does not stop flowing outward. On the contrary, the storage chamber 5 is connected with the outside of the storage chamber 5, and the cooling medium in the storage chamber 5 flows outward, which is expected, because only when the cooling medium in the storage chamber 5 flows outward can the cooling medium continuously enter the cooling hole 3, continuously cool down, and realize a continuous rotor cooling process.

[0110] In order to achieve the communication between the storage chamber 5 and the outside of the storage chamber 5, see Figure 5 In some embodiments, the storage chamber 5 is connected to the outside of the storage chamber 5 through the sealing structure 6. In this case, the storage chamber 5 is connected to the outside by utilizing the fact that the sealing structure 6 is not absolutely tight. Since no other structure is required, the structure is relatively simple. This method of connecting the storage chamber 5 to the outside of the storage chamber 5 through the sealing structure 6 is particularly suitable for the case where the sealing structure 6 is not so tight and there is a certain amount of leakage (such as the comb seal portion 61 mentioned below); or, as an alternative, see Figure 6In some embodiments, at least one of the housing 1 and the rotor 2 is provided with a leakage hole 7, and the storage chamber 5 is connected to the outside of the storage chamber 5 through the leakage hole 7. In this case, the leakage hole 7 is specially provided outside the sealing structure 6 to achieve leakage of the cooling medium in the storage chamber 5. In this case, the leakage flow can be controlled by designing the flow area of ​​the leakage hole 7, and the leakage flow affects the flow of the cooling medium flowing into the cooling hole 3 and the force F2 (which can be called the balancing force F2) used to balance the gas force F1. Therefore, it is convenient to reduce the fluctuation of the cooling medium flow and more accurately control the cooling medium flow for cooling the rotor 2. This is conducive to more accurate control of the temperature of the rotor and the size of the balancing force F2. This method of providing the leakage hole 7 is particularly suitable for a sealing structure 6 with tight sealing and almost no leakage (such as the graphite ring sealing portion 62 and the lip sealing portion 63 mentioned below).

[0111] In the aforementioned embodiments, the sealing structure 6 for sealing the storage cavity 5 can adopt various structural forms.

[0112] For example, in some embodiments, the sealing structure 6 includes at least one of a comb-teeth seal 61, a graphite ring seal 62, and a lip-shaped seal 63. The comb-teeth seal 61, the graphite ring seal 62, and the lip-shaped seal 63 are all sealing structures capable of achieving a good sealing effect. Therefore, when the sealing structure 6 includes at least one of the comb-teeth seal 61, the graphite ring seal 62, and the lip-shaped seal 63, it can effectively seal the storage chamber 5, facilitate the cooling medium to build up pressure in the storage chamber 5, and balance the gas force.

[0113] Compared to the graphite ring seal 62 and lip seal 63, the comb-teeth seal 61 provides a less tight seal, making it easier for the storage chamber 5 to communicate with the outside, enabling a continuous cooling process. Compared to the comb-teeth seal 61, the graphite ring seal 62 and lip seal 63 offer stronger and tighter sealing, facilitating a better seal, establishing high pressure, and balancing gas forces. Furthermore, the graphite ring seal 62 exhibits a certain degree of self-lubrication and a low coefficient of expansion, making it less susceptible to thermal expansion and further facilitating improved sealing, high pressure, and gas balance.

[0114] When the sealing structure 6 includes the comb-teeth seal portion 61, the comb-teeth seal portion 61 may be configured as at least one of the following:

[0115] The comb seal portion 61 is located between the axial end surface of the rotor 2 and the housing 1;

[0116] The comb seal portion 61 is located between the circumferential surface of the rotor 2 and the housing 1;

[0117] The number of teeth of the comb seal portion 61 is 3 to 5;

[0118] The gap between the tooth tips of the comb-teeth seal 61 and the rotor 2 is 5% to 15% of the diameter of the cooling hole 3 .

[0119] When the comb-teeth seal 61 is located between the axial end face of the rotor 2 and the housing 1 , the comb-teeth seal 61 can seal the storage chamber 5 in the axial direction, thereby facilitating the cooling medium to build up pressure in the storage chamber 5 and balance the gas force.

[0120] When the comb-teeth seal 61 is located between the circumferential surface of the rotor 2 and the housing 1 , the comb-teeth seal 61 can seal the storage chamber 5 in the radial direction, thereby facilitating the pressure buildup of the cooling medium in the storage chamber 5 and balancing the gas force.

[0121] When the number of teeth of the comb-tooth sealing part 61 is 3 to 5, the number of teeth of the comb-tooth sealing part 61 is more appropriate, which can achieve effective sealing and a certain leakage, and can make the amount of cooling medium and the pressure in the storage chamber 5 sufficient, which is conducive to achieving better effects in both cooling and gas force balance.

[0122] When the gap between the tooth tips of the comb-tooth seal 61 and the rotor 2 is 5% to 15% (for example, 6%, 8%, 10%, 12%, 13% or 14%) of the diameter of the cooling hole 3, the gap between the comb-tooth seal 61 and the rotor 2 is more appropriate, which can achieve both effective sealing and a certain leakage, and can ensure that the amount of cooling medium and the pressure in the storage chamber 5 are sufficient, which is conducive to achieving better effects in both cooling and gas force balance.

[0123] In addition, when the sealing structure 6 includes a graphite ring sealing portion 62, the graphite ring sealing portion 62 can be located between the axial end surface of the rotor 2 (e.g., the intake end surface 27) and the housing 1, or between the circumferential surface of the rotor 2 and the housing 1. When the graphite ring sealing portion 62 is located between the axial end surface of the rotor 2 and the housing 1, the advantages of the graphite ring sealing portion 62 can be more fully utilized. The graphite ring sealing portion 62 can be tightly attached to the axial end surface of the rotor 2, achieving a better sealing effect.

[0124] Furthermore, when the sealing structure 6 includes a lip seal 63, the lip seal 63 can be located either between the axial end surface of the rotor 2 (e.g., the suction end surface 27) and the housing 1, or between the circumferential surface of the rotor 2 and the housing 1. When the lip seal 63 is located between the circumferential surface of the rotor 2 and the housing 1, the advantages of the lip seal 63 can be more fully utilized, and the lip seal 63 can be tightly wrapped around the circumferential end surface of the rotor 2, achieving a better sealing effect.

[0125] In the aforementioned embodiments, the cooling hole 3 may be directly connected to the inlet 15 for supplying the cooling medium into the compressor 10, or may be indirectly connected to the inlet 15 for supplying the cooling medium into the compressor 10 through other structures.

[0126] For example, see Figure 2 and Figure 3 In some embodiments, a guide groove 4 is provided on the axial end surface of the rotor 2. The guide groove 4 is connected to the cooling hole 3 and guides the cooling medium to flow into the cooling hole 3. In this way, the cooling medium can be conveniently guided into the cooling hole 3 through the guide groove 4. In this case, the cooling hole 3 is not directly connected to the inlet 15 for the cooling medium to enter the housing 1, nor is it connected to the inlet 15 through a connecting pipe. Therefore, the connecting pipe and structure can be simplified. Moreover, the design of the guide groove 4 can conveniently achieve communication between the relatively rotating cooling hole 3 and the inlet 15, as well as communication between a large number of cooling holes 3 and the inlet 15.

[0127] For example, see Figure 2 and Figure 3 In some embodiments, the drainage groove 4 is annular. The annular drainage groove 4 can always be connected to the non-rotating inlet 15 during the rotation of the rotor 2. Therefore, the cooling hole 3 located on the rotating rotor 2 and rotating with the rotor 2 can be easily connected to the non-rotating inlet 15 during the rotation of the rotor 2, so that a better cooling effect can be achieved with a simpler structure.

[0128] There may be one or at least two cooling holes 3 communicating with the diversion groove 4. When there are at least two cooling holes 3 communicating with the diversion groove 4, the advantages of the diversion groove 4 can be more fully utilized, and based on a relatively simple structure, the communication between the at least two cooling holes 3 and the relatively rotating inlet 15 can be conveniently achieved. Among them, the at least two cooling holes 3 communicating with the diversion groove 4 can be located in the diversion groove 4 and arranged at intervals along the circumferential direction. In other words, at least two cooling holes 3 arranged at intervals along the circumferential direction can be provided in the diversion groove 4. In this way, the at least two cooling holes 3 arranged along the circumference of the rotor 2 are both connected to the relatively rotating inlet 15 through the same diversion groove 4, resulting in a simpler structure.

[0129] The size of the drainage groove 4 in the aforementioned embodiments can be set in various ways.

[0130] For example, in some embodiments, the width of the diversion groove 4 is greater than or equal to the diameter of the cooling hole 3. In this case, the width of the diversion groove 4 is more appropriate, which makes it easier to arrange the cooling holes 3 in the diversion groove 4, so that the cooling holes 3, especially at least two cooling holes 3, can be easily connected to the inlet 15 through the diversion groove 4.

[0131] For another example, in some embodiments, the depth of the drainage groove 4 is 0.8 to 1.2 times (e.g., 0.9, 1.0, or 1.1 times) the diameter of the cooling hole 3. In this case, the depth of the drainage groove 4 is relatively appropriate, allowing a certain amount of cooling medium to be stored to meet cooling needs while also allowing excess cooling medium to overflow, cooling the entire surface of the drainage groove 4 and assisting in sealing, reducing leakage and improving efficiency. All of these factors help reduce the adverse effects of thermal expansion of the rotor 2 on the performance of the compressor 10, effectively improving the performance of the compressor 10.

[0132] For example, in some embodiments, the radial distance between the outer edge of the drainage groove 4 and the tooth root 25 of the tooth 23 on the rotor 2 is greater than or equal to L, where L is 3-5 mm (e.g., 4, 4.2, or 4.5 mm). This optimal radial distance between the drainage groove 4 and the tooth 23 facilitates sufficient cooling of the tooth 23 while preventing the cooling medium in the drainage groove 4 from leaking into the tooth groove. This would prevent excessive cooling medium from entering the tooth groove, occupying space required for gas compression and affecting the compression effect.

[0133] Next, combine Figures 1-6 The embodiments shown are used to further introduce the present application.

[0134] First, let’s introduce Figure 1-Figure 5 The embodiment shown.

[0135] like Figure 1-Figure 5 As shown, in this embodiment, the compressor 10 is a screw compressor, which includes a housing 1 , a rotor 2 and a bearing 8 .

[0136] Among them, the outer shell 1 includes a shell 11 and a support portion 12. The shell 11 is a rotating body, which is hollow inside and open at both ends, so that the shell 1 has openings at both axial ends, and the corresponding openings are respectively used for the compressed gas to flow into and out of the compressor 10, forming an intake port 13 and an exhaust port 14. A step portion is provided on the side of the shell 11 near the exhaust port 14, and the axial surface of the corresponding step portion constitutes a first end face 17, which is used to gap fit with the exhaust end face 26 of the rotor 2. The support portion 12 is arranged in the shell 11 and is located on the side near the intake port 13, and protrudes radially inward from the inner wall of the shell 11. The end face of the support portion 12 facing the exhaust port 14 constitutes a second end face 18, which is used to gap fit with the intake end face 27 of the rotor 2.

[0137] The rotor 2 is provided with teeth 23 and is concentrically and rotatably arranged in the housing 1 through the bearing 8. Figures 1-4As shown, in this embodiment, the rotor 2 comprises a working section 22 and two supporting sections 21. The two supporting sections 21 are connected to the axial ends of the working section 22 and have diameters smaller than the working section 22. The two supporting sections 21 engage with the axial holes of the housing 1 and are supported on the housing 1 via bearings 8. Specifically, the supporting section 21 on the intake port 13 side extends into the support portion 12 and is supported by the bearing 8, while the supporting section 21 on the exhaust port 14 side extends into the axial hole at the exhaust port 14 and is supported by the bearing 8 (thrust bearing). The supporting section 21 is axially fixed at the corresponding bearing 8. In this way, the rotor 2 is rotatably disposed as a whole within the housing 1. The working section 22 is located between the two supporting sections 21, and its minimum diameter is greater than the maximum diameter of the two supporting sections 21. Thus, the working section 22 has two axial end faces, which respectively oppose the first end face 17 and the second end face 18 described above and are clearance-fitted with each other, forming the exhaust end face 26 and the intake end face 27. A plurality of (ie at least three) teeth 23 are provided between the exhaust end face 26 and the intake end face 27 and spaced apart along the circumferential direction. The tooth tops 24 of the teeth 23 are in clearance fit with the inner wall of the housing 1 to compress the gas and increase the gas pressure.

[0138] In order to reduce the thermal expansion of the rotor 2, as Figure 1-Figure 5 As shown, in this embodiment, the housing 1 is provided with an inlet 15 and a nozzle 16 , and the rotor 2 is provided with a drainage groove 4 and a cooling hole 3 .

[0139] Among them, the inlet 15 is located on the side of the shell 11 close to the exhaust port 14, and is connected to the lubricating oil supply source to introduce lubricating oil into the shell 1 for lubrication and cooling. This means that, in this embodiment, the lubricating oil is not only used as a lubricant, but also as a cooling medium.

[0140] The nozzle 16 is communicated with the inlet 15 and faces the working section 22 of the rotor 2 , so that lubricating oil used as a cooling medium can be sprayed onto the outer surface of the working section 22 through the nozzle 16 to cool the rotor 2 .

[0141] The diversion groove 4 is used to connect the inlet 15 and the cooling hole 3 so that the lubricating oil used as the cooling medium can flow into the cooling hole 3 to cool the rotor 2. Figure 2 and Figure 4 As shown, in this embodiment, the drainage groove 4 is located on the exhaust end surface 26 of the rotor 2 and is annular and concentric with the exhaust end surface 26. The outer edge of the drainage groove 4 is at least 3 to 5 mm away from the tooth roots 25 of the rotor 2's teeth 23 to prevent lubricating oil from leaking into the tooth grooves and affecting the normal compression process. Furthermore, the width of the drainage groove 4 is equal to or slightly larger than the diameter of the cooling hole 3, and the depth of the drainage groove 4 is 0.8 to 1.2 times the diameter of the cooling hole 3. This effectively balances the required lubricating oil flow rate with workability.

[0142] The cooling holes 3 are located inside the rotor 2 and are used to guide the lubricating oil to flow inside the rotor 2 for cooling. Figures 1-4 As shown, in this embodiment, the rotor 2 is provided with a plurality of cooling holes 3. These cooling holes 3 are radially located within the drainage grooves 4 and spaced apart along the circumference of the rotor 2, corresponding one-to-one with the plurality of teeth 23 spaced apart along the circumference of the rotor 2. Furthermore, each cooling hole 3 extends axially along the rotor 2 and penetrates the working section 22 of the rotor 2. In other words, each cooling hole 3 axially penetrates both the exhaust end face 26 and the intake end face 27 of the rotor 2. On the exhaust end face 26, each cooling hole 3 communicates with the inlet 15 through the drainage grooves 4. Consequently, lubricating oil can enter the cooling holes 3 from the exhaust end face 26, flow axially along the rotor 2, and ultimately flow out of the rotor 2 from the intake end face 27. This allows the lubricating oil to flow in the opposite direction of the compressed gas discharge, aligning with the characteristics of the working section 22, where the temperature rise is most significant, and the exhaust side, where the temperature is higher. Consequently, the rotor 2, particularly the working section 22 of the rotor 2, which compresses the gas, can be effectively cooled. Furthermore, on the exhaust end surface 26, each cooling hole 3 is located approximately directly below the tooth tip 24 of the corresponding tooth 23. This effectively cools the tooth tip 24, where it is thickest, and maximizes the cooling effect. In this embodiment, the diameters of the cooling holes 3 are equal, ranging from 3 to 12 mm, effectively balancing lubricant flow and machinability.

[0143] like Figure 1 and Figure 5As shown, in this embodiment, a storage cavity 5 is provided between the suction end surface 27 and the support portion 12, and the corresponding storage cavity 5 is sealed by two comb-tooth seals 61 serving as a sealing structure 6, wherein one comb-tooth seal 61 is located between the suction end surface 27 of the rotor 2 and the support portion 12, and the other comb-tooth seal 61 is located between the circumferential surface of the support segment 21 on the suction side of the rotor 2 and the support portion 12, and the number of teeth of the two comb-tooth seals 61 is 3 to 5 (for example, 4), and the gap between the tooth tips of the two comb-tooth seals 61 and the suction end surface 27 is 5% to 15% (for example, 6%, 8%, 10%, 12% or 13%) of the diameter of the cooling hole 3. In this way, the lubricating oil flowing out of the cooling hole 3 can flow into the storage chamber 5 and, through the gaps between the two comb-teeth seals 61, into the housing 1, achieving a continuous cooling process. Furthermore, the lubricating oil in the storage chamber 5 can be effectively sealed, establishing oil pressure and applying a force F2 toward the exhaust port 14 to the rotor 2, offsetting a portion of the gas force F1 toward the intake port 13, effectively balancing the gas forces and reducing the bearing load. Furthermore, because the storage chamber 5 is sealed, the drainage groove 4 and the cooling hole 3 are filled with lubricating oil. This lubricating oil overflows from the drainage groove 4 and fills the exhaust end gap (i.e., the gap between the exhaust end face 26 and the first end face 17), forming an oil film seal and performing auxiliary sealing. This can further reduce leakage, thereby more effectively improving the efficiency of the compressor 10 and enabling the compressor 10 to meet the operating requirements of a higher compression ratio operating condition under the same gap value conditions.

[0144] In this embodiment, since the rotor 2 is cooled both inside and outside by lubricating oil, and the internal cooling fully considers the changing trend of the cooling demand of the rotor 2 in the axial and radial directions (for example, the temperature on the suction side in the axial direction is higher and the teeth 23 in the radial direction are the most difficult to cool, etc.), the rotor 2 can be fully cooled, the thermal expansion of the rotor 2 can be effectively reduced, and the risk of mechanical friction, locking or leakage caused by the thermal expansion of the rotor 2 is reduced, thereby improving the structure and working reliability of the compressor 10, improving the efficiency of the compressor 10, and improving the performance of the compressor 10.

[0145] Furthermore, in this embodiment, oil film auxiliary sealing can be performed at the exhaust end face 26 to further reduce the exhaust end face gap and reduce the leakage, thereby further improving the efficiency and working reliability of the compressor 10.

[0146] Furthermore, by providing a sealed storage chamber 5 on the suction side, a hydraulic thrust mechanism can be formed, which effectively balances the gas force and reduces the bearing load based on a relatively simple structure.

[0147] In summary, the compressor 10 of this embodiment can achieve sufficient cooling of the rotor 2 and effective balance of gas forces based on a relatively simple structure, which not only reduces the risk of friction and locking, but also reduces the leakage, and effectively improves reliability and efficiency, thereby achieving better performance.

[0148] Next, we will introduce Figure 6 The embodiment shown.

[0149] like Figure 6 As shown, the compressor 10 in this embodiment is Figure 1-Figure 5 The compressor 10 in the embodiment shown has substantially the same structure as above, except that the sealing structure 6 for sealing the storage chamber 5 no longer includes two comb-teeth sealing parts 61, but includes a graphite ring sealing part 62 and a lip-shaped sealing part 63, and an external leakage hole 7 is additionally provided on the housing 1. Figure 6 As can be seen, the graphite ring seal 62 is positioned between the intake end face 27 and the support portion 12 (specifically, the second end face 18), closely fitting against the intake end face 27. Furthermore, the lip seal 63 is positioned between the circumferential surface of the intake-side support segment 21 and the support portion 12, tightly enveloping the circumferential surface of the support segment 21. The leakage hole 7 is provided on the support portion 12, connecting the storage chamber 5 with the interior of the housing 1. This structure not only effectively establishes oil pressure and balances gas forces thanks to the tight sealing effect of the graphite ring seal 62 and the lip seal 63, but also precisely controls the lubricating oil flow rate through the leakage hole 7, reducing lubricating oil flow fluctuations. This not only improves the accuracy of rotor temperature control but also makes the balancing force F2 generated by the oil pressure more precise and stable. The diameter of the leakage hole 7 can be set according to the amount of lubricating oil.

[0150] Based on the compressor 10 of the aforementioned embodiments, the present application further provides a refrigeration device. As an example, the corresponding refrigeration device may be an air conditioner or a refrigerator.

[0151] The above description is merely an exemplary embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A compressor (10), characterized in that: include: A housing (1) having an air intake port (13) and an air exhaust port (14); and A rotor (2) is rotatably disposed in the housing (1) to compress gas entering from the air intake (13) and discharge the compressed gas from the air exhaust (14). Cooling holes (3) are provided inside the rotor (2). The cooling holes (3) guide a cooling medium to flow inside the rotor (2) to cool the rotor (2).

2. The compressor (10) according to claim 1, characterized in that The compressor (10) is configured as at least one of the following: The cooling hole (3) deviates from the central axis of the rotor (2); A guide groove (4) is provided on the axial end surface of the rotor (2), the guide groove (4) is in communication with the cooling hole (3) and guides the cooling medium to flow toward the cooling hole (3); A storage cavity (5) is provided between the rotor (2) and the housing (1), the storage cavity (5) being in communication with the cooling hole (3) to receive the cooling medium flowing out of the cooling hole (3), and a sealing structure (6) is provided between the rotor (2) and the housing (1), the sealing structure (6) sealing the storage cavity (5) so that the cooling medium in the storage cavity (5) exerts a force on the rotor (2) in a direction from the air intake (13) to the air discharge (14); At least two cooling holes (3) are provided inside the rotor (2); The diameter of the cooling hole (3) is 3-12 mm; The housing (1) is further provided with a nozzle (16), and the nozzle (16) is used to guide a cooling medium to the outer surface of the rotor (2) to cool the rotor (2); The cooling medium includes lubricating oil.

3. The compressor (10) according to claim 2, characterized in that At least two cooling holes (3) are provided inside the rotor (2), and the at least two cooling holes (3) are arranged at intervals along the circumference of the rotor (2).

4. The compressor (10) according to claim 3, characterized in that The rotor (2) is provided with at least two teeth (23) distributed along the circumferential direction, and in the circumferential direction of the rotor (2), the at least two cooling holes (3) correspond one-to-one to the at least two teeth (23) distributed along the circumferential direction.

5. The compressor (10) according to claim 4, characterized in that On the exhaust end face (26) of the rotor (2), each cooling hole (3) is located directly below the tooth top (24) of the corresponding tooth (23). The exhaust end face (26) of the rotor (2) is the axial end face of the rotor (2) facing the exhaust port (14) and having an axial clearance fit with the housing (1).

6. The compressor (10) according to claim 2, characterized in that The drainage trough (4) is constructed as at least one of the following: The drainage groove (4) is annular; The width of the drainage groove (4) is greater than or equal to the diameter of the cooling hole (3); The depth of the drainage groove (4) is 0.8 to 1.2 times the diameter of the cooling hole (3); The distance between the outer edge of the drainage groove (4) and the tooth root (25) of the tooth (23) on the rotor (2) in the radial direction of the rotor (2) is greater than or equal to L, and L is 3-5 mm.

7. The compressor (10) according to claim 6, characterized in that At least two cooling holes (3) are arranged at intervals along the circumferential direction in the annular drainage groove (4).

8. The compressor (10) according to claim 2, characterized in that The axial end face of the rotor (2) provided with the drainage groove (4) is the exhaust end face (26) of the rotor (2), and the exhaust end face (26) of the rotor (2) is the axial end face of the rotor (2) facing the exhaust port (14) and having an axial clearance fit with the housing (1).

9. The compressor (10) according to claim 2, characterized in that The storage chamber (5) is communicated with the outside of the storage chamber (5) so that the cooling medium flowing from the cooling hole (3) into the storage chamber (5) flows to the outside of the storage chamber (5); and / or the sealing structure (6) includes at least one of a comb seal portion (61), a graphite ring seal portion (62) and a lip seal portion (63).

10. The compressor (10) according to claim 9, characterized in that The storage chamber (5) is in communication with the outside of the storage chamber (5) via the sealing structure (6); or, at least one of the housing (1) and the rotor (2) is provided with an external leakage hole (7), and the storage chamber (5) is in communication with the outside of the storage chamber (5) via the external leakage hole (7).

11. The compressor (10) according to claim 9, characterized in that The sealing structure (6) includes the comb-teeth sealing portion (61), and the comb-teeth sealing portion (61) is configured as at least one of the following: The comb-teeth seal portion (61) is located between the axial end surface of the rotor (2) and the housing (1); The comb-teeth seal portion (61) is located between the circumferential surface of the rotor (2) and the housing (1); The number of teeth of the comb-teeth sealing portion (61) is 3 to 5; The gap between the tooth tip of the comb tooth seal portion (61) and the rotor (2) is 5% to 15% of the diameter of the cooling hole (3).

12. The compressor (10) according to claim 9, characterized in that The sealing structure (6) includes the graphite ring sealing portion (62), and the graphite ring sealing portion (62) is located between the axial end surface of the rotor (2) and the housing (1); and / or the sealing structure (6) includes the lip sealing portion (63), and the lip sealing portion (63) is located between the circumferential surface of the rotor (2) and the housing (1).

13. The compressor (10) according to claim 2, characterized in that The storage chamber (5) is located on a side of the intake end face (27) of the rotor (2) that is away from the exhaust port (14), and the intake end face (27) of the rotor (2) is an axial end face of the rotor (2) that faces the intake port (13) and is in axial clearance fit with the housing (1).

14. The compressor (10) according to any one of claims 1 to 13, characterized in that The cooling hole (3) is configured as at least one of the following: At least part of the cooling hole (3) extends along the axial direction and / or radial direction of the rotor (2); The cooling hole (3) passes through the exhaust end surface (26) of the rotor (2), and the exhaust end surface (26) of the rotor (2) is an axial end surface of the rotor (2) facing the exhaust port (14) and having an axial clearance fit with the housing (1); The cooling hole (3) passes through the air intake end surface (27) of the rotor (2), and the air intake end surface (27) of the rotor (2) is an axial end surface of the rotor (2) facing the air intake port (13) and having an axial clearance fit with the housing (1).

15. The compressor (10) according to claim 14, characterized in that The cooling hole (3) extends along the axial direction of the rotor (2); and / or the cooling medium flows into the cooling hole (3) from the exhaust end face (26); and / or the cooling medium flows out of the cooling hole (3) from the intake end face (27).

16. A refrigeration device, characterized in that: Comprising a compressor (10) as described in any one of claims 1 to 15.

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