A rotor assembly, a compressor, and an air conditioner

Abstract

This invention provides a rotor assembly, a compressor, and an air conditioner. The rotor assembly includes a first rotor having a first shaft core hole. The first rotor includes a plurality of first teeth, each first tooth having a root circle radius of r1, and the first shaft core hole having a radius of R. c1 The second rotor can mesh with the first rotor; the center distance between the first and second rotors when they mesh is A; where, (r1-R c1 The ratio of (r1-R) / A ranges from 9% to 25.3%. Specifically, the first rotor is configured with a first shaft core hole, which allows for the mounting of a shaft body; that is, the first rotor and the shaft body are separate structures, facilitating the machining of the first rotor. c1 The ratio of ) / A is limited to the range of 9% to 25.3%, which can ensure the rigidity of the first tooth without affecting the area utilization coefficient of the first tooth in the first rotor, reduce the deformation of the first tooth during operation, and improve the working reliability of the first rotor.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more particularly to a rotor assembly, a compressor, and an air conditioner. Background Technology

[0002] A compressor typically has a pair of parallel helical rotors housed within the compressor's casing. As the rotors rotate, this casing periodically increases and decreases, causing it to periodically connect and close with the intake and exhaust ports, thus completing the processes of intake, compression, and exhaust.

[0003] The existing helical rotor has a separate toothed part from the rotor shaft. In order to ensure the assembly and positioning of the helical rotor and the rotor shaft, the helical rotor needs to reserve a certain space in the inner hole for assembly with the rotor shaft. Due to the existence of the inner hole, the transmission reliability of the helical rotor in actual operation is affected, which reduces the working reliability of the helical rotor. Summary of the Invention

[0004] This invention provides a rotor assembly, a compressor, and an air conditioner to address the problem of low operational reliability of existing rotors.

[0005] In a first aspect, embodiments of the present invention provide a rotor assembly, comprising:

[0006] A first rotor has a first shaft core hole; the first rotor includes a plurality of first teeth, each first tooth having a root circle radius of r1, and the first shaft core hole having a radius of R. c1 ;as well as

[0007] A second rotor, which can mesh with the first rotor; the center distance between the first rotor and the second rotor when they mesh is A.

[0008] Among them, (r1-R c1 The ratio of ) / A ranges from 9% to 25.3%.

[0009] In one optional embodiment of the present invention, the tip circle radius of each first tooth is R1, and the pitch circle radius of each first tooth is R. t1 , where (R1-R t1 The ratio of ) / A ranges from 18.2% to 25.3%.

[0010] In one optional embodiment of the present invention, the ratio of the working length L1 of the first tooth to the tip circle diameter D1 of the first tooth, L1 / D1, ranges from 1.0 to 1.9.

[0011] In one optional embodiment of the present invention, the torsion angle of the first rotor is in the range of 250° to 320°.

[0012] In one optional embodiment of the present invention, the second rotor has a second shaft core hole; the second rotor includes a plurality of second teeth, the first teeth being capable of meshing with the second teeth; the root radius of each second tooth is r2, and the radius of the second shaft core hole is R. c2 Among them, (r2-R) c2 The ratio of ) / A ranges from 8.7% to 23%.

[0013] In one optional embodiment of the present invention, the tip circle radius of each second tooth is R2, and the pitch circle radius of each second tooth is R. t2 , where (R2-R t2 The ratio of ) / A ranges from 1.8% to 3.4%.

[0014] In one optional embodiment of the present invention, the ratio of the working length L2 of the second tooth to the tip circle diameter R2 of the second tooth, L2 / R2, ranges from 1.0 to 1.8.

[0015] In one optional embodiment of the present invention, it further includes:

[0016] The first shaft body is inserted through the first shaft core hole;

[0017] The second shaft body is inserted through the second shaft core hole;

[0018] A third rotor, having the same tooth profile as the first rotor but with the opposite rotation direction, is mounted on the first shaft; and

[0019] The fourth rotor has the same tooth profile as the second rotor but rotates in the opposite direction, and is mounted on the second shaft; the third rotor can mesh with the fourth rotor.

[0020] Secondly, embodiments of the present invention also provide a compressor, including the rotor assembly described above.

[0021] Thirdly, embodiments of the present invention also provide an air conditioner, including the compressor described above.

[0022] The rotor assembly, compressor, and air conditioner provided in this invention include a first rotor and a second rotor that mesh with each other. When the first rotor and the second rotor rotate in mesh, they cooperate with the compressor housing to achieve the functions of intake, compression, and exhaust. The first rotor is configured with a first shaft core hole, which allows for the mounting of a shaft body; that is, the first rotor and the shaft body are separate structures, facilitating the machining of the first rotor. The root circle radius of the first rotor is set to r1, and the radius of the first shaft core hole is set to R. c1And combining the center distance A when the first rotor and the second rotor mesh, (r1-R) c1 The ratio of ) / A is limited to the range of 9% to 25.3%, which can ensure the rigidity of the first tooth without affecting the area utilization coefficient of the first tooth in the first rotor, reduce the deformation of the first tooth during operation, and improve the working reliability of the first rotor. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are merely some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without any creative effort.

[0024] To better understand the present invention and its beneficial effects, the following description will be made in conjunction with the accompanying drawings, wherein the same reference numerals denote the same parts in the following description.

[0025] Figure 1 This is a first partial schematic diagram of a compressor provided in an embodiment of the present invention;

[0026] Figure 2 An exploded view of the rotor assembly provided in an embodiment of the present invention;

[0027] Figure 3 The end face profile diagram of the first rotor and the second rotor when meshing is provided for an embodiment of the present invention;

[0028] Figure 4 A cross-sectional view of a rotor assembly having four rotors provided for an embodiment of the present invention;

[0029] Figure 5 The end face profile diagram of the first rotor and the second rotor when meshing is provided for an embodiment of the present invention;

[0030] Figure 6 A schematic diagram of the profile shape of the first rotor and the second rotor when they are meshing, provided for a specific embodiment of the present invention;

[0031] Figure 7 This is a second partial schematic diagram of a compressor provided in an embodiment of the present invention. Attached image description:

[0033] 100. Compressor;

[0034] 10. Casing; 11. First exhaust port; 12. Intake port; 13. Second exhaust port;

[0035] 20. Rotor assembly; 21. First rotor; 211. First tooth; 212. First shaft core hole; 22. Second rotor; 221. Second tooth; 222. Second shaft core hole; 23. First shaft body; 231. First shaft axis; 24. Second shaft body; 25. Third rotor; 26. Fourth rotor. Detailed Implementation

[0036] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the protection scope of the present invention.

[0037] In this document, references to "embodiment" or "implementation" mean that a particular feature, structure, or characteristic described in connection with an embodiment or implementation may be included in at least one embodiment of the invention. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0038] It should be noted that the terms "first," "second," etc., in the specification, claims, and drawings of this invention are used to distinguish different objects, not to describe a specific order, and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, features defined with "first" or "second" may explicitly or implicitly include one or more features. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0039] This invention provides a rotor assembly, compressor, and air conditioner to address the problem of low operational reliability in existing rotor systems. The following description, in conjunction with the accompanying drawings, will illustrate this.

[0040] This invention provides a rotor assembly suitable for use in a compressor. The compressor can be a screw compressor, such as an opposed screw compressor. For example, please refer to [link to relevant documentation]. Figure 1 , Figure 1This is a partial schematic diagram of a compressor provided in an embodiment of the present invention. The compressor 100 may include a housing 10 and a rotor assembly 20, wherein the rotor assembly 20 includes a first rotor 21 and a second rotor 22, and the housing 10 can accommodate the first rotor 21 and the second rotor 22. It is understood that the housing 10 has a receiving space for accommodating the first rotor 21 and the second rotor 22. When the first rotor 21 and the second rotor 22 mesh and rotate within the housing 10, they compress the gas within the receiving space to the outside of the housing 10. Exemplarily, the housing 10 also has a first exhaust port 11 and an intake port 12, both of which are connected to the receiving space for accommodating the first rotor 21 and the second rotor 22. It should be noted that the intake port 12 is used to transfer gas outside the housing 10 to the receiving space within the housing 10 when the first rotor 21 and the second rotor 22 mesh and rotate, and the first exhaust port 11 is used to compress the gas within the receiving space of the housing 10 to the outside of the housing 10 when the first rotor 21 and the second rotor 22 mesh and rotate, thereby realizing the intake, compression, and exhaust processes of the compressor 100.

[0041] In this embodiment of the invention, the first rotor 21 and the second rotor 22 mesh with each other. The first rotor 21 can be a male rotor, and the second rotor 22 can be a female rotor. The first rotor 21, as a male rotor, can be understood as the active rotor, and the second rotor 22, as a female rotor, can be understood as the driven rotor. For example, the first rotor 21 can be connected to a drive assembly such as a motor (including but not limited to a permanent magnet motor). The first rotor 21 can be driven to rotate by the drive assembly. Simultaneously, the rotation of the first rotor 21 drives the second rotor 22 to rotate, thereby realizing the intake, compression, and exhaust processes of the compressor 100.

[0042] Please continue reading. Figure 1The rotor assembly 20 also includes a first shaft 23 and a second shaft 24. The first rotor 21 is supported by the first shaft 23 and is connected to the drive assembly via the first shaft 23. The drive assembly can drive the first shaft 23 to rotate, and the first shaft 23 can rotate together with the first rotor 21 it supports along the first axis 231 of the first shaft 23. That is, the first rotor 21 can rotate within the housing 10 along the first axis 231. The second rotor 22 is supported by the second shaft 24, which is rotatably supported on the housing 10. In this case, the second rotor 22 can be fixed on the second shaft 24, and when the second rotor 22 meshes with the first rotor 21 and the first rotor 21 rotates, the second rotor 22 and the second shaft 24 can rotate together. Alternatively, the second rotor 22 can be supported by the second shaft 24 and can rotate on the second shaft 24. The second shaft 24 is fixedly connected to the housing 10, and when the second rotor 22 meshes with the first rotor 21 and the first rotor 21 rotates, the second rotor 22 can rotate around the second shaft 24. Please continue reading for more details. Figure 1 When there is only the first rotor 21 on the first shaft 23 and only the second rotor 22 on the second shaft 24, the first exhaust port 11 and the air inlet can be respectively set at both ends of the housing 10 along the first axis 231 of the first shaft 23, in accordance with the meshing exhaust and intake pattern of the first rotor 21 and the second rotor 22.

[0043] Understandably, the first rotor 21 includes multiple first teeth 211, and the second rotor 22 includes multiple second teeth 221. The meshing between the first rotor 21 and the second rotor 22 is the meshing of the first teeth 211 and the second teeth 221. It is also understandable that, in some terminology, the first tooth 211 can be called the first helical blade or the first male blade, and the second tooth 221 can be called the second helical blade or the second female blade.

[0044] In existing related technologies, to facilitate the manufacturing of the first rotor 21, the first shaft 23, the second rotor 22, and the second shaft 24, the first rotor 21 and the first shaft 23 are manufactured separately, and the second rotor 22 and the second shaft 24 are manufactured separately and then assembled separately. That is, the first rotor 21 and the first shaft 23 are separate structures, and the second rotor 22 and the second shaft 24 are also separate structures. Please refer to... Figure 2 , Figure 2This is an exploded view of the rotor assembly provided in an embodiment of the present invention. Taking the first rotor 21 as an example, when the first rotor 21 and the first shaft 23 are made into a separable structure, in order to ensure the assembly between the first rotor 21 and the first shaft 23, a first shaft core hole 212 needs to be provided on the first rotor 21 for the first shaft 23 to pass through. It can be understood that the first shaft core hole 212 penetrates the first rotor 21 along the axial direction of the first rotor 21. The first shaft 23 and the first rotor 21 can be assembled and fixed together by a key connection, or the first shaft core hole 212 of the first rotor 21 can be fixed together by an interference fit.

[0045] However, it should be noted that during the actual operation of the first rotor 21, the diameter of the first shaft core hole 212 will affect the rigidity of the first tooth 211 in the first rotor 21. In existing related technologies, during operation of the first rotor 21 and the second rotor 22, the first tooth 211 in the first rotor 21 and the second tooth 221 in the second rotor 22 are prone to deformation due to their low rigidity, which reduces the operational reliability of the first rotor 21 and the second rotor 22.

[0046] Based on this, the rotor assembly 20 provided in this embodiment of the invention can effectively reduce rotor deformation during operation and improve the operational reliability of the rotor assembly 20. For example, please refer to... Figure 3 and combined Figure 2 , Figure 3 This is an end face profile diagram of the first rotor and the second rotor meshing according to an embodiment of the present invention. The root circle radius of the first tooth portion 211 in the first rotor 21 is r1, and the radius of the first shaft core hole 212 in the first rotor 21 is R. c1 When the first rotor 21 and the second rotor 22 are meshing, the center distance between the first rotor 21 and the second rotor 22 is A. Because the center of the first rotor 21 is hollowed out, the overall stiffness of the first rotor 21 is reduced to a certain extent, especially the root stiffness of the first tooth 211. Therefore, in order to control the deformation of the first tooth 211 of the first rotor 21 during processing and actual operation, and to improve the root stiffness of the first tooth 211, the rotor assembly 20 provided in this embodiment of the invention uses (r1-R) to... c1 The ratio of (r1-R) / A is set between 9% and 25.3% to improve the stiffness of the first tooth 211 in the first rotor 21. c1 This ratio range of (r1-R) / A effectively ensures that there is a certain effective width between the root circle of the first tooth 211 and the first shaft core hole 212, thereby improving the root stiffness of the first tooth 211 and making it less prone to deformation. Furthermore, in the first rotor 21, (r1-R) c1This ratio range of (r1-R) / A will not reduce the area utilization coefficient of the working surface of the first tooth 211 due to the excessive width between the root circle of the first tooth 211 and the first shaft core hole 212, thus not affecting the displacement of the compressor 100 using the rotor assembly 20 provided in this embodiment of the invention, that is, the displacement of (r1-R) / A in the first rotor 21. c1 This ratio range of ) / A can, under the premise that the area factor of the first tooth 211 remains unchanged, ensure the width of the tooth root of the first tooth 211 as much as possible, thereby ensuring the rigidity of the first tooth 211 and not affecting the working efficiency of the rotor assembly 20. It can be understood that the working surface of the first tooth 211 refers to the surface of the first tooth 211 used for compressing and transmitting gas.

[0047] Among them, (r1-R) c1 The ratio of ) / A is set between 10% and 20.3%, and the first tooth 211 has better stiffness within this range.

[0048] In some other embodiments, to further improve the stiffness of the first tooth 211 of the first rotor 21, the pitch circle radius R of the first tooth 211 can be subtracted from the tip circle radius R1 of the first tooth 211. t1 The ratio of the center distance A when the first rotor 21 and the second rotor 22 are meshing is set between 18.2% and 25.3%, that is, (R1-R2) / R2 = 18.2% to 25.3%. t1 The ratio of (R1-R) / A is set between 18.2% and 25.3%, thereby effectively improving the stiffness of the first tooth 211 of the first rotor 21. Specifically, (R1-R) / A can be... t1 The ratio of ) / A is set between 20.2% and 23.3%, and the first tooth 211 has better stiffness within this range.

[0049] It should be noted that the stiffness of the first tooth 211 is also related to the working length and the tip circle diameter of the first tooth 211. Under the same displacement, the larger the ratio between the working length and the tip circle diameter of the first tooth 211, the smaller the tip circle diameter of the first tooth 211 is, making the shape of the working section of the entire first rotor 21 similar to a "slender shape", which affects the stiffness of the first rotor 21.

[0050] Based on this, please refer to Figure 4 and Figure 5 , Figure 4 A cross-sectional view of a rotor assembly having four rotors is provided for an embodiment of the present invention. Figure 5This is an end face profile diagram of the first rotor and the second rotor meshing according to an embodiment of the present invention. To improve the rigidity of the first tooth 211, in some other embodiments, the ratio of the working length L1 of the first tooth 211 to the tip circle diameter D1 of the first tooth 211, L1 / D1, is set between 1.0 and 1.9. This range of L1 / D1 ensures that the working section of the first rotor 21 is not too thin, thereby improving the rigidity of the working section of the first rotor 21 without reducing the displacement of the rotor assembly 20, and thus improving the operational reliability of the rotor assembly 20.

[0051] The first tooth 211 has a helical shape. The stiffness of the first tooth 211 is related to its torsion angle, which is also related to the torsion angle of the first rotor 21. The torsion angle of the first rotor 21 characterizes the degree of twisting of the first rotor 21 from the intake end face to the exhaust end face. When the ratio of the working length of the first tooth 211 to the tip circle diameter of the first tooth 211 is constant, the magnitude of the torsion angle will affect the force on the working tooth surface of the first tooth 211, thereby affecting the stiffness of the first tooth 211 to a certain extent. In order to improve the stiffness of the first tooth 211 without affecting the working efficiency of the rotor assembly 20, the torsion angle of the first rotor 21 is set between 250° and 320°. This range allows the working tooth surface of the first tooth 211 to be subjected to less force, thus improving the stiffness of the first tooth 211 to a certain extent.

[0052] Please continue reading. Figure 2 In the rotor assembly 20 provided in this embodiment of the invention, the second rotor 22 is a rotor that cooperates with the first rotor 21. The first rotor 21 is a male rotor and the second rotor 22 is a female rotor. As a female rotor, when the second rotor 22 and the second shaft 24 are separate structures, the second rotor 22 is provided with a second shaft core hole 222 for assembly with the second shaft 24. During the actual operation of the second rotor 22, the size of the hole diameter of the second shaft core hole 222 will also affect the rigidity of the second tooth 221 in the second rotor 22.

[0053] Based on this, please refer to section 3. The root circle radius of the second tooth portion 221 in the second rotor 22 is r2, and the radius of the second shaft core hole 222 in the second rotor 22 is R. c2When the first rotor 21 and the second rotor 22 are meshing, the center distance between the first rotor 21 and the second rotor 22 is A. Because the second rotor 22 has a hollowed-out center, its overall stiffness is reduced to some extent, especially the root stiffness of the second tooth portion 221. Therefore, to control the deformation of the second tooth portion 221 during machining and actual operation, and to improve the root stiffness of the second tooth portion 221, the rotor assembly 20 provided in this embodiment of the invention uses (r2-R) to... c2 The ratio of (r2-R) / A is set between 8.7% and 23% to improve the stiffness of the second tooth 221 in the second rotor 22. c2 This ratio range of (r2-R) / A effectively ensures that there is a certain effective width between the root circle of the second tooth 221 and the second shaft core hole 222, thereby improving the root stiffness of the second tooth 221 and making it less prone to deformation. Furthermore, in the second rotor 22, ((r2-R) / A... c2 This ratio range of (r2-R) / A will not reduce the area utilization coefficient of the working surface of the second tooth 221 due to the excessive width between the root circle of the second tooth 221 and the second shaft core hole 222, thus not affecting the displacement of the compressor 100 using the rotor assembly 20 provided in this embodiment of the invention, that is, the displacement of (r2-R) in the second rotor 22. c2 This ratio range of ) / A can, under the premise that the area factor of the second tooth 221 remains unchanged, ensure the width of the tooth root of the second tooth 221 as much as possible, thereby ensuring the rigidity of the second tooth 221 and not affecting the working efficiency of the rotor assembly 20. It can be understood that the working surface of the second tooth 221 refers to the surface of the second tooth 221 used for compressing and transmitting gas.

[0054] Among them, (r2-R) c2 The ratio of ) / A is set between 8.8% and 21%, and the second tooth 221 has better stiffness within this range.

[0055] In some other embodiments, to further improve the stiffness of the second tooth 221 of the second rotor 22, the pitch circle radius R of the second tooth 221 can be subtracted from the tip circle radius R2 of the second tooth 221. t2 The ratio of the center distance A when the first rotor 21 and the second rotor 22 are meshing is set between 1.8% and 3.4%, that is, (R2-R... t2 The ratio of (R2-R) / A is set between 1.8% and 3.4%, thereby effectively improving the stiffness of the second tooth 221 of the second rotor 22. Specifically, (R2-R) / A can be... t2 The ratio of ) / A is set between 2.2% and 3.1%, and the second tooth 221 has better stiffness within this range.

[0056] It should be noted that the stiffness of the second tooth 221 is also related to the working length of the second tooth 221 and the tip circle diameter of the second tooth 221. Under the same displacement, the larger the ratio between the working length of the second tooth 221 and the tip circle diameter of the second tooth 221, the smaller the tip circle diameter of the second tooth 221 is, making the shape of the working section of the entire second rotor 22 similar to a "slender shape", which affects the stiffness of the second rotor 22.

[0057] Based on this, please continue reading Figure 4 and Figure 5 To improve the rigidity of the second tooth 221, in some other embodiments, the ratio of the working length L2 of the second tooth 221 to the tip circle diameter D2 of the second tooth 221, L2 / D2, is set between 1.0 and 1.8. This range of L2 / D2 ensures that the working section of the second rotor 22 is not too thin, thereby improving the rigidity of the working section of the second rotor 22 without reducing the displacement of the rotor assembly 20, and thus improving the operational reliability of the rotor assembly 20. Specifically, to further enhance the rigidity of the second tooth 221, the ratio of L2 / D2 can be set to 1.0.

[0058] The second tooth 221 has a helical shape, meaning the second rotor 22 has a torsion angle. The torsion angle of the second rotor 22 represents the degree of twisting of the second rotor 22 from the intake end face to the exhaust end face. Since the second rotor 22 is a female rotor, it needs to cooperate with the male rotor (i.e., the first rotor 21). Therefore, the torsion angle of the second rotor 22 can be calculated based on the number of teeth of the second rotor 22, the number of teeth of the first rotor 21, and the torsion angle of the first rotor 21. The torsion angle of the first rotor 21 divided by the torsion angle of the second rotor 22 is equal to the number of teeth of the second rotor 22 divided by the number of teeth of the first rotor 21. Thus, the torsion angle of the second rotor 22 can be calculated based on the number of teeth of the second rotor 22, the number of teeth of the first rotor 21, and the torsion angle of the first rotor 21.

[0059] It should be noted that, based on the analysis of application scenarios, thermodynamic performance, and rotor processing characteristics, the rotor centers of the first rotor 21 and the second rotor 22 provided in this embodiment of the invention are penetrated and used in conjunction with the shaft. In order to ensure that the stiffness of the first rotor 21 and the second rotor 22 are nearly identical and to ensure good thermodynamic performance, the number of teeth of the first rotor 21 is set to 5 and the number of teeth of the second rotor 22 is set to 6.

[0060] By setting the parameters of the first rotor 21 and the second rotor 22 as described above, the stiffness of the first rotor 21 and the second rotor 22 can be effectively improved.

[0061] Specifically, based on the parameter ranges of the first rotor 21 and the second rotor 22 mentioned above, a specific embodiment of the first rotor 21 and the second rotor 22 is given. For example, the rotational speed of the first rotor 21 is 2950 rpm, ensuring a theoretical displacement of 50.4551 m³ / h. 3 At approximately / h, for the first rotor 21, the number of teeth of the first rotor 21 is set to 5, the tip circle diameter of the first rotor 21 (i.e., the tip circle diameter D1 of the first tooth portion 211) is set to 90.5000 mm, and the pitch circle diameter of the first rotor 21 (i.e., the pitch circle diameter D of the first tooth portion 211) is set to 90.5000 mm. t1 The diameter D of the first shaft core hole 212 of the first rotor 21 is set to 61.8182 mm. c1 The working length of the first rotor 21 (i.e., the working length L1 of the first tooth 211) is set to 50 mm, the ratio L1 / D1 of the tip circle diameter of the first rotor 21 (i.e., the tip circle diameter D1 of the first tooth 211) is set to 1.0000, the working length of the first rotor 21 (i.e., the working length L1 of the first tooth 211) is set to 90.5000, and the torsion angle of the first rotor 21 is set to 270.0000°.

[0062] For the second rotor 22, the number of teeth of the second rotor 22 is set to 6, the tip circle diameter of the second rotor 22 (i.e., the tip circle diameter D2 of the second tooth portion 221) is set to 75.0000 mm, and the pitch circle diameter of the second rotor 22 (i.e., the pitch circle diameter D of the second tooth portion 221) is set to 75.0000 mm. t2 The diameter D of the second shaft core hole 222 of the second rotor 22 is set to 74.1818 mm. c2 The working length of the second rotor 22 (i.e., the working length L2 of the second tooth 221) is set to 35 mm, the ratio L2 / D2 of the tip circle diameter of the second rotor 22 (i.e., the tip circle diameter D2 of the second tooth 221) is set to 1.0000, the working length of the second rotor 22 (i.e., the working length L2 of the second tooth 221) is set to 90.5000, and the torsion angle of the second rotor 22 is set to 225.0000°.

[0063] Furthermore, it should be noted that the first rotor 21 and the second rotor 22 satisfy the meshing principle, which means that when the teeth of the male and female rotors are in contact at the contact point, they only have relative sliding in the tangential direction and no relative velocity in the normal direction. Therefore, the first rotor 21 and the second rotor 22 do not impact each other during transmission.

[0064] The reserved clearance refers to the meshing clearance between the male and female rotors. In actual operation, the compressor 100 does not allow the tooth surfaces to contact each other in order to reduce tooth surface wear, but instead reserves a certain clearance.

[0065] Based on the specific parameters of the first rotor 21 and the second rotor 22, and assuming that the tooth profiles of the first rotor 21 and the second rotor 22 satisfy the meshing principle, and after reserving a clearance of 0.02 mm to 0.03 mm, a certain tooth curve is selected to obtain the actual profile coordinate data of the first rotor 21 and the second rotor 22, namely, the coordinate data of the male rotor and the coordinate data of the female rotor. The center of the female rotor is taken as the coordinate center. The actual coordinate data of the male rotor and the female rotor are as follows (unit: mm):

[0066]

[0067]

[0068]

[0069]

[0070]

[0071]

[0072]

[0073]

[0074]

[0075]

[0076]

[0077]

[0078]

[0079]

[0080]

[0081]

[0082]

[0083]

[0084]

[0085]

[0086] The specific profile shape of the first rotor 21 and the second rotor 22 when they mesh can be obtained from the above coordinate points, such as Figure 6 As shown, Figure 6 This is a schematic diagram of the profile shape of the first rotor and the second rotor when they are meshing, provided for a specific embodiment of the present invention.

[0087] After the parameters of the first rotor 21 and the second rotor 22 are set as described above, the first rotor 21 and the second rotor 22 can have sufficient rigidity, have small deformation during actual operation, and can achieve smaller clearance meshing, thereby effectively improving performance and operational reliability.

[0088] For example, please refer to Figure 7 , Figure 7This is a second partial schematic diagram of a compressor provided in an embodiment of the present invention. The rotor assembly 20 may further include a third rotor 25 and a fourth rotor 26. It is understood that a screw compressor including a first rotor 21, a second rotor 22, a third rotor 25, and a fourth rotor 26 can be called a four-rotor screw compressor. The third rotor 25 can be a male rotor, and the fourth rotor 26 can be a female rotor. The first rotor 21 meshes with the second rotor 22, and the third rotor 25 meshes with the fourth rotor 26. It is understood that the third rotor 25 is supported by a first shaft 23, and the fourth rotor 26 is supported by a second shaft 24. The third rotor 25 and the first rotor 21 have the same tooth profile but opposite rotation directions. It is understood that the third rotor 25 and the first rotor 21 have the same tooth profile, meaning that the aforementioned parameters are the same, i.e., the number of teeth, the tip circle diameter, the pitch circle diameter, the shaft core hole diameter, the working length, and the torsion angle are the same. The rotation direction of the fourth rotor 26 is the same as the tooth profile of the second rotor 22 but opposite. It is understandable that the third rotor 25 has the same tooth profile as the first rotor 21, meaning that all the aforementioned parameters are the same, namely, the number of teeth, the tip circle diameter, the pitch circle diameter, the shaft core hole diameter, the working length, and the torsion angle are the same. It is also understandable that the first shaft 23 simultaneously supports the first rotor 21 and the third rotor 25, and the second shaft 24 simultaneously supports the second rotor 22 and the fourth rotor 26. The adjacent end faces of the first rotor 21 and the third rotor 25 have small gaps, such as 0.1 mm, 0.2 mm, or 0.3 mm. The adjacent end faces of the second rotor 22 and the fourth rotor 26 also have small gaps, such as 0.1 mm, 0.2 mm, or 0.3 mm. In this scenario, when the first rotor 21 and the second rotor 22 mesh and rotate, and when the third rotor 25 and the fourth rotor 26 mesh and rotate, opposite axial forces are generated between the first rotor 21 and the third rotor 25, and opposite axial forces are generated between the second rotor 22 and the fourth rotor 26. This can also be understood as opposite axial flows being generated between the first rotor 21 and the third rotor 25, and opposite axial flows being generated between the second rotor 22 and the fourth rotor 26. Due to the symmetry of the axial forces, the opposite axial forces generated between the first rotor 21 and the third rotor 25 can cancel each other out, and the opposite axial forces generated between the second rotor 22 and the fourth rotor 26 can also cancel each other out. This is understandable, as... Figure 7 As shown, the suction port 12 of the four-rotor compressor 100 can be located between the first rotor 21 and the third rotor 25, and the exhaust port can be set to two, namely, the first exhaust port 11 is located at the end of the first rotor 21 away from the third rotor 25, and the second exhaust port 13 is located at the end of the third rotor 25 away from the first rotor 21.

[0089] The compressor 100 in one or more of the above embodiments can be used in air conditioners.

[0090] On the other hand, embodiments of the present invention also provide an air conditioner, which includes a compressor 100 as defined in combination with one or more of the above embodiments.

[0091] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0092] The rotor assembly, compressor, and air conditioner provided in the embodiments of the present invention have been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of the present invention. The description of the above embodiments is only for the purpose of helping to understand the method and core ideas of the present invention. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the ideas of the present invention. Therefore, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A rotor assembly, characterized in that, include: A first rotor has a first shaft core hole; the first rotor includes a plurality of first teeth, each first tooth having a root circle radius of r1, and the first shaft core hole having a radius of R. c1 ; as well as A second rotor, which can mesh with the first rotor; the center distance between the first rotor and the second rotor when they mesh is A. Among them, (r1- R c1 The ratio of ) / A ranges from 9% to 25.3%; The tip circle radius of each of the first teeth is R1, and the pitch circle radius of each of the first teeth is R. t1 , where (R1-R t1 The ratio of () / A ranges from 18.2% to 25.3%; The ratio of the working length L1 of the first tooth to the tip circle diameter D1 of the first tooth, L1 / D1, ranges from 1.0 to 1.

9. The second rotor has a second shaft core hole; the second rotor includes a plurality of second teeth, the first teeth being capable of meshing with the second teeth; the root circle radius of each second tooth is r2, and the radius of the second shaft core hole is R. c2 Among them, (r2- R) c2 The ratio of ) / A ranges from 8.7% to 23%; The tip circle radius of each second tooth is R2, and the pitch circle radius of each second tooth is R. t2 , where (R2-R t2 The ratio of () / A ranges from 1.8% to 3.4%; The ratio of the working length L2 of the second tooth to the tip circle diameter D2 of the second tooth, L2 / D2, ranges from 1.0 to 1.

8.

2. The rotor assembly according to claim 1, characterized in that, The torsion angle of the first rotor ranges from 250° to 320°.

3. The rotor assembly according to claim 1, characterized in that, Also includes: The first shaft body is inserted through the first shaft core hole; The second shaft body passes through the second shaft core hole; The third rotor has the same tooth profile as the first rotor but rotates in the opposite direction, and the third rotor is mounted on the first shaft. as well as The fourth rotor has the same tooth profile as the second rotor but rotates in the opposite direction, and is mounted on the second shaft; the third rotor can mesh with the fourth rotor.

4. A compressor, characterized in that, Includes the rotor assembly as described in any one of claims 1-3.

5. An air conditioner, characterized in that, Includes the compressor as described in claim 4.

Images