Compressor and refrigeration equipment

Abstract

The invention 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 a refrigeration device. 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, leading to mechanical friction, locking or leakage, causing damage to the compressor structure, shutdown or reduced efficiency, and affecting the performance of the compressor. Summary of the invention

[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, which includes:

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

[0007] The rotor is rotatably arranged in the shell to compress the gas entering from the air intake port and discharge the compressed gas from the air exhaust port. The rotor is provided with cooling holes inside 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, the guide groove is connected to the cooling hole, and guides the cooling medium to flow to the cooling hole;

[0011] A storage cavity is provided between the rotor and the housing, the storage cavity is communicated with the cooling hole to receive the cooling medium flowing out of the cooling hole, and a sealing structure is provided between the rotor and the housing, the sealing structure seals the storage cavity, so that the cooling medium in the storage cavity exerts a force on the rotor in a direction from the air intake port 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 introduce a 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, at least two teeth distributed along the circumferential direction are provided on the rotor, 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, 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.

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

[0020] The drainage groove 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 disposed in the annular drainage groove and are spaced apart from each other in 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-teeth seal portion, and the comb-teeth seal portion is configured as at least one of the following:

[0029] The comb teeth 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%~15% of the cooling hole diameter.

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

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

[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 drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. 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 paying 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 partial 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. Description of reference numerals:

[0051] 10. Compressor;

[0052] 1. Shell; 11. Shell; 12. Support portion; 13. Air inlet; 14. Air outlet; 15. Inlet; 16. Nozzle; 17. First end surface; 18. Second end surface;

[0053] 2. rotor; 21. support section; 22. working section; 23. tooth; 24. tooth top; 25. tooth root; 26. exhaust end face; 27. intake end face;

[0054] 3. Cooling holes;

[0055] 4. Drainage trough;

[0056] 5. Storage cavity;

[0057] 6. Sealing structure; 61. Comb seal; 62. Graphite ring seal; 63. Lip seal;

[0058] 7. Leakage hole;

[0059] 8. Bearings. DETAILED DESCRIPTION

[0060] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present application and its application or use. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without carrying out creative work are within the scope of protection of this application.

[0061] 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.

[0062] In the description of the present application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings, and are only for the convenience of describing the present 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, and therefore cannot be understood as limiting the scope of protection of the present application; the directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

[0063] In the description of the present application, it should be understood that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of the present application.

[0064] 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.

[0065] 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 rotor of the compressor by improving the structure of the compressor, thereby improving the performance of the compressor.

[0066] Figure 1-Figure 6 The structure of the compressor in the present application is shown exemplarily.

[0067] See also Figure 1-Figure 6In the present application, the compressor 10 includes a housing 1 and a rotor 2. The housing 1 has an air intake port 13 and an air discharge port 14 for compressed gas to enter and discharge, respectively. The rotor 2 is rotatably disposed in the housing 1 to compress the gas entering from the air intake port 13 and discharge the compressed gas from the air discharge port 14.

[0068] The rotor 2 has an exhaust end face 26 and an intake end face 27. Both the exhaust end face 26 and the intake end face 27 are axial end faces of the rotor 2 used for axial clearance fit with the housing 1, and the two are arranged in sequence along the direction from the exhaust port 14 to the intake port 13, respectively close to and far away from the exhaust port 14. 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 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, and the corresponding clearance can be called the exhaust end clearance. The intake end face 27 and the second end face 18 are opposite to each other and have a clearance fit, and the corresponding clearance can be called the intake end clearance.

[0069] Specifically, see Figure 1 In some embodiments, the rotor 2 is provided with teeth 23. The teeth 23 protrude radially outward and cooperate with the teeth 23 of another rotor 2 (for example, another rotor 2 of a dual-rotor compressor) or the housing 1 to form a chamber with a variable volume, so that during the rotation of the rotor 2, the gas can be compressed by the change in volume at the teeth 23. In this case, the exhaust end face 26 and the intake end face 27 are usually the end faces at both ends of the axial direction of the portion of the rotor 2 provided with the teeth 23.

[0070] More specifically, see Figure 1-Figure 4 In some embodiments, the rotor 2 includes a working section 22 and two supporting sections 21. The teeth 23 are arranged on the working section 22. Usually, the working section 22 is provided with at least two (for example, 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 supported on the housing 1 by bearings 8 respectively, so that the rotor 2 is rotatably arranged in the housing 1 as a whole. Usually, of the two supporting sections 21, the supporting section 21 located on the exhaust port 14 side is axially fixed at the bearing 8.

[0071] The diameters of the two supporting segments 21 are smaller than the diameter of the working segment 22, so that the connection between the working segment 22 and the two supporting segments 21 forms an axial end face, which is respectively matched with the first end face 17 and the second end face 18 in a clearance, thereby forming an exhaust end face 26 and an intake end face 27. At this time, the exhaust end face 26 is the axial end face of the working segment 22 close to the exhaust port 14, and is also the axial end face of the rotor 2 provided with the teeth 23 and closest to the exhaust port 14. The intake end face 27 is the axial end face of the working segment 22 away from the exhaust port 14, and is also the axial end face of the rotor 2 provided with the teeth 23 and farthest from the exhaust port 14.

[0072] The clearance at the exhaust end, the clearance at the intake end, 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, while if they are too small, they are prone to friction or even locking, causing structural damage or even shutdown.

[0073] During the operation of the compressor 10, a large amount of heat is generated, which causes the temperature of the rotor 2, especially the side of the rotor 2 close to the exhaust port 14 (which may be referred to as the exhaust side), to rise. When the temperature of the rotor 2 rises, it will expand due to the heat, and the higher the temperature, the greater the expansion. The thermal expansion of the rotor is likely to 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. 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 face 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.

[0074] It can be seen that the rotor 2 of the compressor 10 is easily expanded by heat during the operation of the compressor 10, causing mechanical friction, locking or leakage, resulting in structural damage to the compressor, shutdown or reduced efficiency, and affecting the performance of the compressor.

[0075] 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 Figure 1-Figure 6In the present application, a cooling hole 3 is provided inside the rotor 2 of the compressor 10 , and the cooling hole 3 guides the cooling medium to flow inside the rotor 2 to cool the rotor 2 .

[0076] By providing cooling holes 3 and introducing 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 thus 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.

[0077] In particular, since the cooling holes 3 are arranged inside the rotor 2, the cooling medium can be guided to flow inside the rotor 2 to cool the rotor 2 inside the rotor 2. Compared with the method of spraying the cooling medium on the outer surface of the rotor 2 to cool 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 and more effectively improving the performance of the compressor 10. Of course, while the cooling holes 3 are arranged inside the rotor 2, a nozzle 16 can also be arranged on the housing 1 to guide the cooling medium to 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 inside the rotor 2, but also by spraying the cooling medium on the outer surface of the rotor 2 to cool the rotor 2, thereby realizing a cooling method combining internal and external cooling. This cooling method combining internal and external cooling can achieve a better cooling effect. 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.

[0078] It can be seen that by providing 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.

[0079] In the present application, the cooling medium can be various fluids (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, easier to seal, less likely to leak under the same gap, and 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, and more effectively reduce the thermal expansion of the rotor 2 during the operation of the compressor 10, thereby improving the performance of the compressor 10.

[0080] In addition, in the present application, the cooling holes 3 can be arranged in various ways.

[0081] 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 with the case where only one cooling hole 3 is provided, when at least two cooling holes 3 are provided inside the rotor 2, since the number of cooling holes 3 is greater, the cooling medium can be guided to flow through more places inside the rotor 2, and more parts of the rotor 2 can be cooled. 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.

[0082] 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 part 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, and the rotor 2 is effectively cooled. Among them, 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 it is not easy to damage the teeth 23. Therefore, it is more convenient to set 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 the cooling hole 3 is constructed to extend along the axial direction of the rotor 2, which is convenient to achieve a better cooling effect based on a simpler structure and more effectively improve the performance of the compressor 10.

[0083] Among them, when the cooling hole 3 extends along the axial direction, the cooling medium in the cooling hole 3 can flow along the direction from the exhaust port 14 to the intake port 13, or can flow along the direction from the intake port 13 to the exhaust port 14. Compared with the case where the cooling medium flows along the direction from the intake port 13 to the exhaust port, when the cooling medium flows along 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 succession. Since the cooling medium temperature is relatively low when flowing through the exhaust side, the higher temperature exhaust side can be cooled more effectively. Moreover, when flowing through the intake side, although the cooling medium temperature increases, the intake side temperature is relatively low and the cooling demand is relatively low. Therefore, the cooling medium can still meet the cooling demand of the intake side temperature well 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 a better cooling effect can be achieved.

[0084] For another example, the position of the cooling hole 3 is not limited, and it may be located at the center of the rotor 2 or not. 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 take into account the cooling requirements of the center and outer surface of the rotor 2, and effectively cool the inside of the rotor 2 while also cooling 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 Figure 1-Figure 4 In the case where 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 a cooling medium is sprayed externally or a cooling hole 3 is 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 only the cooling hole 3 is provided in the center of the rotor 2, then under the same diameter condition, the cooling hole 3 is far away from the tooth 23, and the cooling medium flowing through the cooling hole 3 is difficult to effectively cool the tooth 23, especially the tooth top 24 of the tooth 23, and the cooling effect is poor. If the cooling hole 3 is deviated from the central axis of the rotor 2, the cooling hole 3 is closer to the tooth 23, and the tooth 23, especially the tooth top 24, can be cooled more effectively. Therefore, it is conducive to achieving a more sufficient cooling effect, thereby further reducing the thermal expansion of the rotor 2 and improving the performance of the compressor 10.

[0085] The number of the cooling holes 3 deviating from the central axis of the rotor 2 may also be one or at least two.

[0086] As an example, see Figure 2-Figure 3In some embodiments, 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. 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 deviated from the center of the rotor 2, and is located radially outside 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 play a certain cooling role 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.

[0087] It can be seen that by providing at least two cooling holes 3 arranged at intervals along the circumference of the rotor 2 inside the rotor 2, it is beneficial to more fully cool the rotor 2, especially the rotor 2 with teeth 23. Therefore, it is more beneficial to reduce the thermal expansion of the rotor 2 and improve the performance of the compressor 10.

[0088] Further, 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 teeth 23 of the rotor 2 distributed along the circumference in a one-to-one manner. In this way, each tooth 23 is provided with a corresponding cooling hole 3 in the circumference of the rotor 2, and 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 the thermal expansion of the rotor 2 and improving the performance of the compressor 10.

[0089] 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 .

[0090] As mentioned above, for the rotor 2 with teeth 23, the thickness is the largest at the tooth top 24 of the tooth 23, and the cooling difficulty is the greatest. The cooling hole 3 is constructed to be located on the exhaust end surface 26, directly below the tooth top 24 of the corresponding tooth 23. This 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.

[0091] 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 the cooling hole 3 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 away from 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 deviates 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.

[0092] In the above embodiments, the diameter of the cooling hole 3 can be 3-12 mm, for example, 4, 6, 7, 9, 10 or 11 mm. At this time, the diameter of the cooling hole 3 is more appropriate, which is convenient for processing and can effectively meet the flow demand of the cooling medium in most cases, thereby achieving a better cooling effect.

[0093] Also, see Figure 1-Figure 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 .

[0094] The cooling hole 3 penetrates 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. In this way, the performance of the compressor 10 can be improved more conveniently and effectively, 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, so as to achieve more sufficient cooling of the rotor 2 and more effectively reduce 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 to further reduce leakage. All of these are conducive to further improving the performance of the compressor 10.

[0095] As mentioned above, the end face of the rotor 2 which is provided with the teeth 23 and is 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 where the temperature rise is the highest, the thermal expansion is the most obvious, and the leakage is most likely to occur. 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 where the temperature rise is the highest, the thermal expansion is the most obvious, and the leakage is most likely to occur. This is conducive to further reducing the risks of mechanical friction, locking and leakage, and more effectively improving the performance of the compressor 10.

[0096] 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 to cool and oil-seal the corresponding suction end face. 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] 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 .

[0098] When the cooling hole 3 penetrates the exhaust end face 26 , the cooling medium can flow into or out of the cooling hole 3 from the exhaust end face 26 , and when the cooling hole 3 penetrates the intake end face 27 , the cooling medium can flow into or out of the cooling hole 3 from the intake end face 27 .

[0099] Among them, when the cooling hole 3 penetrates 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 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 higher temperature can be more fully cooled to achieve better cooling effect, and therefore, it is more conducive to improving the performance of the compressor 10.

[0100] When the cooling hole 3 penetrates 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.

[0101] 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, which affects the reliability and life of the bearing 8 and the compressor 10.

[0102] In the related art, a balancing piston is usually provided on the suction side, and the balancing piston uses high-pressure fluid to apply a force in the opposite direction of the gas force F1 to the rotor 2 to balance the gas force F1 and reduce the load on the bearing 8. However, this method of using a balancing piston to balance the gas force F1 requires the configuration of special pipelines and drive cylinders and other components, and the structure is relatively complicated.

[0103] The cooling medium is used to establish 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.

[0104] It can be seen that using a 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 life of the bearing 8 and the compressor 10.

[0105] 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 cavity 5 is provided between the rotor 2 and the housing 1, and the storage cavity 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, and the sealing structure 6 seals the storage cavity 5, so that the cooling medium in the storage cavity 5 applies a force to the rotor 2 along the direction from the air intake port 13 to the exhaust port 14 (i.e., toward the exhaust port 14).

[0106] The storage chamber 5 for receiving the cooling medium flowing out of the cooling hole 3 is sealed by the sealing structure 6, so that the cooling medium flowing out of the cooling hole 3 can establish high pressure in the storage chamber 5, and exert a force F2 on the rotor 2 toward the exhaust side. Since the corresponding force F2 is opposite to the direction of the gas force F1, it can offset a part of the gas force F1 and play a role in balancing the gas force. Therefore, the load on the bearing 8 can be effectively 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. In addition, the storage chamber 5 is sealed by the sealing structure 6, and the cooling medium on the inlet side of the cooling hole 3 can also overflow to form a fluid seal, 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 of the exhaust end face to form a seal and reduce the gap of the exhaust end face. This is conducive to reducing leakage and improving efficiency.

[0107] The storage chamber 5 may be located in various positions 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. Figure 1 as well as Figure 5 and Figure 6 In some embodiments, the storage chamber 5 is located on the side of the suction end face 27 of the rotor 2 away from the exhaust port 14. Since the suction end face 27 is located on the suction side, the storage chamber 5 is provided on the side of the suction end face 27 away from the exhaust port 14, so that the cooling medium in the storage chamber 5 can easily exert a force on the rotor 2 toward the exhaust port 14, thereby realizing the gas force balancing function.

[0108] 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 to the outside of the storage chamber 5, and it is expected that the cooling medium in the storage chamber 5 flows outward, because the cooling medium in the storage chamber 5 flows outward, so that the cooling medium can continuously enter the cooling hole 3, continuously cool down, and realize a continuous rotor cooling process.

[0109] 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. At this time, the storage chamber 5 is connected to the outside by utilizing the characteristic that the sealing structure 6 is not absolutely tight. Since no other structure is required, the structure is relatively simple. This storage chamber 5 is connected to the outside of the storage chamber 5 through the sealing structure 6, which is particularly suitable for the case where the sealing structure 6 is not so tight and has a certain amount of leakage (such as the comb seal 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. At this time, the leakage hole 7 is specially provided outside the sealing structure 6 to achieve the leakage of the cooling medium in the storage chamber 5. In this case, since the leakage flow rate can be controlled by designing the flow area of ​​the leakage hole 7, and the leakage flow rate affects the flow rate 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, it is convenient to reduce the fluctuation of the cooling medium flow rate and more accurately control the cooling medium flow rate for cooling the rotor 2. This is conducive to more accurately controlling the temperature of the rotor and the size of the balancing force F2. This way of setting 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).

[0110] In the above-mentioned embodiments, the sealing structure 6 for sealing the storage cavity 5 can adopt various structural forms.

[0111] For example, in some embodiments, the sealing structure 6 includes at least one of a comb-teeth sealing portion 61, a graphite ring sealing portion 62, and a lip-shaped sealing portion 63. The comb-teeth sealing portion 61, the graphite ring sealing portion 62, and the lip-shaped sealing portion 63 are all sealing structures that can achieve a good sealing effect. Therefore, when the sealing structure 6 includes at least one of the comb-teeth sealing portion 61, the graphite ring sealing portion 62, and the lip-shaped sealing portion 63, it can achieve effective sealing of the storage cavity 5, facilitate the cooling medium to build up pressure in the storage cavity 5, and balance the gas force.

[0112] Among them, compared with the graphite ring seal 62 and the lip seal 63, the seal of the comb-teeth seal 61 is not so tight, which makes it easier for the storage chamber 5 to communicate with the outside and achieve a continuous cooling process. Compared with the comb-teeth seal 61, the graphite ring seal 62 and the lip seal 63 have stronger sealing properties and a tighter sealing effect, which is conducive to achieving a better sealing effect, better establishing high pressure, and balancing gas forces. In addition, the graphite ring seal 62 has a certain self-lubricating function, and a low expansion coefficient, which is less affected by thermal expansion, and is more conducive to improving the sealing effect, establishing high pressure, and performing gas balance.

[0113] 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:

[0114] The comb teeth seal portion 61 is located between the axial end surface of the rotor 2 and the housing 1;

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

[0116] The number of teeth of the comb seal portion 61 is 3 to 5;

[0117] 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 .

[0118] When the comb-teeth seal 61 is located between the axial end surface of the rotor 2 and the housing 1 , the comb-teeth seal 61 can seal the storage chamber 5 in the axial direction, making it easier for the cooling medium to build up pressure in the storage chamber 5 and balance the gas force.

[0119] 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, making it easier for the cooling medium to build up pressure in the storage chamber 5 and balance the gas force.

[0120] 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, so 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.

[0121] When the gap between the tooth tip 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, so 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.

[0122] 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 face (such as the suction end face 27) of the rotor 2 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 face of the rotor 2 and the housing 1, the advantages of the graphite ring sealing portion 62 can be more fully utilized, and the graphite ring sealing portion 62 can be closely attached to the axial end face of the rotor 2 to achieve a better sealing effect.

[0123] In addition, when the sealing structure 6 includes a lip seal 63, the lip seal 63 can be located between the axial end surface (such as the suction end surface 27) of the rotor 2 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 covered on the circumferential end surface of the rotor 2 to achieve a better sealing effect.

[0124] 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.

[0125] As an example, see Figure 2 and Figure 3 In some embodiments, a guide groove 4 is provided on the axial end face of the rotor 2, and the guide groove 4 is connected with the cooling hole 3, and guides the cooling medium to flow to the cooling hole 3. In this way, the cooling medium can be conveniently guided to the cooling hole 3 through the guide groove 4. At this time, 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, so the connecting pipe can be simplified, the structure can be simplified, and the guide groove 4 can be designed to conveniently realize the connection between the relatively rotating cooling hole 3 and the inlet 15, and the connection between more cooling holes 3 and the inlet 15.

[0126] 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 with 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 with the non-rotating inlet 15 during the rotation of the rotor 2, so that a better cooling effect can be achieved based on a simpler structure.

[0127] The cooling hole 3 connected to the drainage groove 4 may be one or at least two. When the number of cooling holes 3 connected to the drainage groove 4 is at least two, the advantages of the drainage groove 4 can be more fully utilized, and based on a relatively simple structure, the connection between 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 connected to the drainage groove 4 can be located in the drainage groove 4 and arranged at intervals along the circumferential direction, that is, at least two cooling holes 3 arranged at intervals along the circumferential direction can be provided in the drainage groove 4, so that the at least two cooling holes 3 arranged along the circumferential direction of the rotor 2 are connected to the relatively rotating inlet 15 through the same drainage groove 4, and the structure is simpler.

[0128] The size of the drainage groove 4 in the above-mentioned embodiments can be set in various ways.

[0129] 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, and it is more convenient to set the cooling hole 3 in the diversion groove 4, so that the cooling hole 3, especially at least two cooling holes 3, can be conveniently connected to the inlet 15 through the diversion groove 4.

[0130] For another example, in some embodiments, the groove depth of the drainage groove 4 is 0.8 to 1.2 times (for example, 0.9, 1.0 or 1.1 times) the diameter of the cooling hole 3. At this time, the groove depth of the drainage groove 4 is relatively appropriate, which can store a certain amount of cooling medium to meet the cooling needs, and it is convenient to overflow the excess cooling medium on the basis of meeting the cooling needs, cool the entire surface of the drainage groove 4 and assist in sealing, reduce leakage, and improve efficiency, which are all conducive to reducing the adverse effects of the thermal expansion of the rotor 2 on the performance of the compressor 10 and effectively improving the performance of the compressor 10.

[0131] For another example, in some embodiments, 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 (for example, 4, 4.2 or 4.5 mm). In this way, the radial distance between the drainage groove 4 and the tooth 23 is relatively appropriate, which is conducive to achieving a more sufficient cooling of the tooth 23 and preventing the cooling medium in the drainage groove 4 from leaking into the tooth groove, so as to avoid excessive cooling medium entering the tooth groove and occupying the space required for gas compression, thereby affecting the compression effect.

[0132] Next, combine Figure 1-Figure 6 The embodiments shown are used to further introduce the present application.

[0133] First, let’s introduce Figure 1-Figure 5 The embodiment shown.

[0134] 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 .

[0135] The housing 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 ends of the axial direction, 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 close to 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 close to 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.

[0136] The rotor 2 is provided with teeth 23 and is rotatably disposed in the housing 1 through a bearing 8 concentrically. Figure 1-Figure 4As shown, in this embodiment, the rotor 2 includes 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 the diameters of the two supporting sections 21 are smaller than the diameter of the working section 22. The two supporting sections 21 are matched with the shaft hole of the housing 1, and are supported on the housing 1 by the bearing 8. Specifically, the supporting section 21 on the side of the air intake port 13 extends into the support portion 12 and is supported by the bearing 8, while the supporting section 21 on the side of the exhaust port 14 extends into the shaft hole at the exhaust port 14 and is supported by the bearing 8 (thrust bearing), and is axially fixed at the corresponding bearing 8. In this way, the rotor 2 is rotatably arranged in the housing 1 as a whole. The working section 22 is located between the two supporting sections 21, and the minimum diameter is greater than the maximum diameter of the two supporting sections 21. In this way, the working section 22 has two axial end faces, which are respectively opposite to the aforementioned first end face 17 and the second end face 18, and are clearance-matched to form the exhaust end face 26 and the intake end face 27. A plurality of (ie at least three) teeth 23 are arranged circumferentially at intervals between the exhaust end face 26 and the intake end face 27. 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.

[0137] In order to reduce the thermal expansion of the rotor 2, 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 .

[0138] 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 makes the lubricating oil not only used as a lubricant, but also used as a cooling medium in this embodiment.

[0139] 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 .

[0140] The drainage 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 face 26 of the rotor 2 and is in a ring shape concentric with the exhaust end face 26. There is a distance of more than 3 to 5 mm between the outer edge of the drainage groove 4 and the tooth root 25 of the tooth 23 of the rotor 2 to prevent the lubricating oil in the drainage groove 4 from leaking into the tooth groove and affecting the normal compression process. In addition, the groove width of the drainage groove 4 is equal to or slightly larger than the diameter of the cooling hole 3, and the groove depth of the drainage groove 4 is 0.8 to 1.2 times the diameter of the cooling hole 3. In this way, the actual required lubricating oil flow rate and machinability can be effectively taken into account.

[0141] 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. Figure 1-Figure 4 As shown, in this embodiment, a plurality of cooling holes 3 are provided in the rotor 2, and the plurality of cooling holes 3 are all located in the drainage groove 4 in the radial direction, and are arranged at intervals along the circumferential direction of the rotor 2, corresponding one by one to the plurality of teeth 23 arranged at intervals along the circumferential direction of the rotor 2, and each of the cooling holes 3 extends along the axial direction of the rotor 2 and penetrates the working section 22 of the rotor 2, that is, each cooling hole 3 penetrates the exhaust end face 26 and the intake end face 27 of the rotor 2 along the axial direction of the rotor 2. On the exhaust end face 26, each cooling hole 3 is connected to the inlet 15 through the drainage groove 4. Based on this, the lubricating oil can enter the cooling hole 3 from the exhaust end face 26, flow along the axial direction of the rotor 2, and finally flow out from the intake end face 27 to the outside of the rotor 2. In this way, the flow direction of the lubricating oil is opposite to the discharge direction of the compressed gas, which is adapted to the characteristics that the temperature rise of the working section 22 is the most obvious and the temperature on the exhaust side is higher. Therefore, the rotor 2 can be effectively cooled, especially the working section 22 of the rotor 2 used for compressing gas. Moreover, on the exhaust end surface 26, each cooling hole 3 is approximately located directly below the tooth top 24 of the corresponding tooth 23, so that the tooth top 24 with the largest thickness can be effectively cooled and the cooling effect can be fully exerted. In this embodiment, the diameters of the cooling holes 3 are equal, both 3 to 12 mm, which can effectively take into account the requirements of lubricating oil flow and machinability.

[0142] 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 used as sealing structures 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 section 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 flow into the housing 1 through the gaps at the two comb-teeth sealing parts 61, thereby realizing a continuous cooling process. In addition, the lubricating oil in the storage chamber 5 can be effectively sealed, and oil pressure is established to apply a force F2 toward the exhaust port 14 to the rotor 2, thereby offsetting a part of the gas force F1 toward the intake port 13, effectively balancing the gas force, and reducing the bearing load. In addition, since the storage chamber 5 is sealed, the drainage groove 4 and the cooling hole 3 will be filled with lubricating oil, and this part of the lubricating oil will overflow from the drainage groove 4, filling the gap at the exhaust end (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. In this way, the leakage can be further reduced, thereby more effectively improving the efficiency of the compressor 10, so that the compressor 10 can meet the operating requirements of a higher compression ratio condition under the same gap value conditions.

[0143] In this embodiment, since the rotor 2 is cooled by lubricating oil both inside and outside, 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 tooth 23 in the radial direction is 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.

[0144] 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.

[0145] 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.

[0146] 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 the reliability and efficiency, thereby achieving better performance.

[0147] Next, let’s introduce Figure 6 The embodiment shown.

[0148] like Figure 6 As shown, the compressor 10 in this embodiment is similar to the above Figure 1-Figure 5 The compressor 10 in the embodiment shown has substantially the same other structures, except that in this embodiment, 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 sealing part 63, and an external leakage hole 7 is additionally provided on the housing 1. Figure 6 It can be seen that the graphite ring sealing part 62 is arranged between the air intake end face 27 and the support part 12 (specifically the second end face 18), and is tightly fitted on the air intake end face 27, and the lip sealing part 63 is arranged between the circumferential surface of the support section 21 on the air intake side and the support section 12, and is tightly covered on the circumferential surface of the support section 21, and the leakage hole 7 is arranged on the support section 12, and connects the storage chamber 5 with the inside of the housing 1. In this way, not only can the oil pressure be effectively established and the gas force balance be performed based on the tight sealing effect of the graphite ring sealing part 62 and the lip sealing part 63, but also the lubricating oil flow rate can be accurately controlled through the leakage hole 7 to reduce the fluctuation of the lubricating oil flow rate. In this way, not only the accuracy of the rotor temperature control can be improved, but also the balancing force F2 generated by the oil pressure can be made more accurate and stable. Among them, the diameter of the leakage hole 7 can be set accordingly according to the amount of lubricating oil.

[0149] Based on the compressor 10 of the above embodiments, the present application further provides a refrigeration device. As an example, the corresponding refrigeration device may be an air conditioner or a refrigerator.

[0150] The above description is only 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 protection scope of the present application.

Claims

1. A compressor (10), characterized in that: include: The housing (1) has 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 port (13) and discharge the compressed gas from the air exhaust port (14); a cooling hole (3) is provided inside the rotor (2); the cooling hole (3) guides 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 connected to 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) so as to receive 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 port (13) to the air discharge port (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 also provided with a nozzle (16), and the nozzle (16) is used to introduce a cooling medium to the outer surface of the rotor (2) so as 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 surface (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 surface (26) of the rotor (2) is an axial end surface of the rotor (2) that faces the exhaust port (14) and is clearance-matched with the housing (1) in the axial direction.

6. The compressor (10) according to claim 2, characterized in that The drainage groove (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 to 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 in communication 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-tooth sealing portion (61), a graphite ring sealing portion (62) and a lip sealing 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) comprises the comb-tooth sealing portion (61), and the comb-tooth sealing portion (61) is constructed 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-tooth 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) comprises the graphite ring sealing portion (62), wherein 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) comprises the lip sealing portion (63), wherein 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 air intake end surface (27) of the rotor (2) that is away from the air outlet (14); the air intake end surface (27) of the rotor (2) is an axial end surface of the rotor (2) that faces the air intake port (13) and is clearance-matched with the housing (1) in the axial direction.

14. The compressor (10) according to any one of claims 1 to 13, characterized in that: The cooling hole (2) 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) penetrates the exhaust end surface (26) of the rotor (2), the exhaust end surface (26) of the rotor (2) being 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 surface (26); and / or the cooling medium flows out of the cooling hole (3) from the intake end surface (27).

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

Images