Double-screw compressor rotor profile and double-screw compressor

Abstract

The invention discloses a double-screw compressor rotor profile and a double-screw compressor, and belongs to the technical field of compressors, the rotor profile comprises a male rotor tooth curve and a female rotor tooth curve, the male rotor tooth curve comprises an A1B1 section, a B1C1 section, a C1D1 section, a D1E1 section, an E1F1 section, an F1G1 section, a G1H1 section and an H1I1 section which are sequentially and smoothly connected; the tooth curve of the female rotor comprises an A2B2 section, a B2C2 section, a C2D2 section, a D2E2 section, an E2F2 section, an F2G2 section, a G2H2 section and an H2I2 section which are sequentially and smoothly connected. The tooth curve of the male rotor is obtained by converting the rack line from a rack coordinate system to a tooth profile coordinate system of the male rotor; and the female rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the female rotor. By means of the sectional tooth curve, the large calculation amount caused by directly optimizing the female rotor profile and the male rotor profile can be avoided, and therefore the design efficiency of the rotor profiles is improved.

Description

Technical Field

[0001] The present application belongs to the technical field of compressors, and in particular relates to a twin-screw compressor rotor profile and a twin-screw compressor. Background Art

[0002] The screw compressor uses a pair of screw rotors that rotate in the casing to achieve gas compression and power transmission. The core part of the screw compressor is the screw rotor. The screw compressor rotor profile (cross-sectional tooth shape) requires as large a volume between teeth as possible, good meshing characteristics and small gas power loss. Therefore, the screw compressor rotor profile is usually composed of multiple curves connected, and the profile is complex and asymmetric; its spiral tooth shape also has the characteristics of large pitch, large helix angle and large tooth height, which determines the level of most of the performance parameters of the compressor.

[0003] At present, when designing the female rotor profile and the male rotor profile, it is necessary to optimize and obtain the female rotor profile and the male rotor profile. The amount of calculation is large when optimizing the female rotor profile and the male rotor profile, which makes the rotor profile design inefficient. Summary of the invention

[0004] Purpose of the invention: This application develops a twin-screw compressor rotor profile, aiming to solve the technical problem of low efficiency in rotor profile design.

[0005] Technical solution: In a first aspect, an embodiment of the present application provides a twin-screw compressor rotor profile, including a male rotor tooth curve and a female rotor tooth curve, wherein:

[0006] The male rotor tooth curve includes a sequence of smoothly connected A1B1 segment, B1C1 segment, C1D1 segment, D1E1 segment, E1F1 segment, F1G1 segment, G1H1 segment and H1I1 segment;

[0007] The female rotor tooth curve includes a segment A2B2, a segment B2C2, a segment C2D2, a segment D2E2, a segment E2F2, a segment F2G2, a segment G2H2 and a segment H2I2 which are smoothly connected in sequence.

[0008] In some embodiments, the male rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the male rotor; the female rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the female rotor;

[0009] The rack line is formed by the meshing of the female rotor and the male rotor, and the rack line includes an AB segment, a BC segment, a CD segment, a DE segment, an EF segment, a FG segment, a GH segment and a HI segment which are smoothly connected in sequence.

[0010] In some embodiments, in the rack line:

[0011] Segment AB is a straight line, the length of which is n1 times the pitch radius of the negative rotor. Segment AB is smoothly connected to segment HI at the starting point, and segment AB is tangent to segment BC at the end point; n1 is a positive number greater than 0.1 and less than or equal to 0.25;

[0012] Segment BC is an arc, and its radius is n2 times the pitch radius of the female rotor. Segment BC is smoothly connected to segment AB at the starting point, and segment BC is tangent to segment CD at the end point; n2 is a positive number greater than 0.05 and less than or equal to 0.25;

[0013] The CD segment is an elliptical arc, the major diameter of which is n3 times the pitch radius of the female rotor, and the minor diameter is n4 times the pitch radius of the female rotor. The CD segment is smoothly connected to the BC segment at the starting point, and the CD segment is tangent to the DE segment at the end point; n3 is a positive number greater than 0.4 and less than or equal to 0.6, and n4 is a positive number greater than 0.15 and less than or equal to 0.35;

[0014] The DE segment is an elliptical arc, the major diameter of which is n5 times the pitch radius of the female rotor, and the minor diameter is n6 times the pitch radius of the female rotor. The DE segment is smoothly connected to the CD segment at the starting point, and the DE segment is tangent to the EF segment at the end point; n5 is a positive number greater than 0.3 and less than or equal to 0.7, and n6 is a positive number greater than 0.1 and less than or equal to 0.3;

[0015] Segment EF is an arc, and its radius is n6 times the pitch radius of the female rotor. Segment EF is smoothly connected to segment DE at the starting point, and segment EF is tangent to segment FG at the end point; n6 is a positive number greater than 0.6 and less than or equal to 0.9;

[0016] The FG segment is an arc, and its radius is n7 times the pitch radius of the female rotor. The FG segment is smoothly connected to the EF segment at the starting point, and is tangent to the GH segment at the end point and is located on the tangent line of the GH segment. n7 is a positive number greater than 0.5 and less than or equal to 0.8.

[0017] The GH segment is an elliptical arc, the major diameter of which is n8 times the pitch radius of the female rotor, and the minor diameter is n9 times the pitch radius of the female rotor. The GH segment is smoothly connected to the FG segment at the starting point, and the GH segment is tangent to the HI segment at the end point; n8 is a positive number greater than 0.6 and less than or equal to 0.9, and n9 is a positive number greater than 0.2 and less than or equal to 0.5;

[0018] Segment HI is an arc with a radius of n. 10 times the pitch radius of the negative rotor, the HI segment is smoothly connected to the GH segment at the starting point, and the HI segment is tangent to the IA segment at the end point; n 10 A positive number greater than 0.3 and less than or equal to 0.5.

[0019] In some embodiments, the gear ratio of the female rotor to the male rotor is 5:3.

[0020] In some embodiments, the male rotor tooth curve further includes an I1J1 segment, and the female rotor tooth curve further includes an I2J2 segment.

[0021] In some embodiments, the male rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the male rotor; the female rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the female rotor;

[0022] The rack line is formed by the meshing of the female rotor and the male rotor, and the rack line includes an AB segment, a BC segment, a CD segment, a DE segment, an EF segment, a FG segment, a GH segment, a HI segment, and an IJ segment which are smoothly connected in sequence.

[0023] In some embodiments, in the rack line:

[0024] Segment AB is a straight line, the length of which is n1 times the pitch radius of the negative rotor. Segment AB is smoothly connected to segment IJ at the starting point, and segment AB is tangent to segment BC at the end point; n1 is a positive number greater than 0.1 and less than or equal to 0.25;

[0025] Segment BC is an arc, and its radius is n2 times the pitch radius of the female rotor. Segment BC is smoothly connected to segment AB at the starting point, and segment BC is tangent to segment CD at the end point; n2 is a positive number greater than 0.05 and less than or equal to 0.25;

[0026] The CD segment is an elliptical arc, the major diameter of which is n3 times the pitch radius of the female rotor, and the minor diameter is n4 times the pitch radius of the female rotor. The CD segment is smoothly connected to the BC segment at the starting point, and the CD segment is tangent to the DE segment at the end point; n3 is a positive number greater than 0.4 and less than or equal to 0.6, and n4 is a positive number greater than 0.15 and less than or equal to 0.35;

[0027] The DE segment is an elliptical arc, the major diameter of which is n5 times the pitch radius of the female rotor, and the minor diameter is n6 times the pitch radius of the female rotor. The DE segment is smoothly connected to the CD segment at the starting point, and the DE segment is tangent to the EF segment at the end point; n5 is a positive number greater than 0.3 and less than or equal to 0.7, and n6 is a positive number greater than 0.1 and less than or equal to 0.3;

[0028] Segment EF is an arc, and its radius is n6 times the pitch radius of the female rotor. Segment EF is smoothly connected to segment DE at the starting point, and segment EF is tangent to segment FG at the end point; n6 is a positive number greater than 0.6 and less than or equal to 0.9;

[0029] The FG segment is an arc, and its radius is n7 times the pitch radius of the female rotor. The FG segment is smoothly connected to the EF segment at the starting point, and is tangent to the GH segment at the end point. n7 is a positive number greater than 0.5 and less than or equal to 0.8;

[0030] The GH segment is an elliptical arc, the major diameter of which is n8 times the pitch radius of the female rotor, and the minor diameter is n9 times the pitch radius of the female rotor. The GH segment is smoothly connected to the FG segment at the starting point, and the GH segment is tangent to the HI segment at the end point; n8 is a positive number greater than 0.6 and less than or equal to 0.9, and n9 is a positive number greater than 0.2 and less than or equal to 0.5;

[0031] Segment HI is an arc with a radius of n. 10 times the pitch radius of the negative rotor, the HI segment is smoothly connected to the GH segment at the starting point, and the HI segment is tangent to the IJ segment at the end point and is located on the tangent line of the IJ segment; n 10 is a positive number greater than 0.3 and less than or equal to 0.5;

[0032] Segment IJ is a straight line, and its length is n 11 times the pitch radius of the negative rotor, the IJ segment is smoothly connected to the HI segment at the starting point, and the IJ segment is tangent to the JA segment at the end point, n 11 A positive number greater than 0.05 and less than or equal to 0.2.

[0033] In some embodiments, the gear ratio of the female rotor to the male rotor is 4:3.

[0034] In some embodiments, a positive rotor tooth curve and a negative rotor tooth curve are generated according to the rack line by a coordinate conversion formula, and the coordinate conversion formula is specifically as follows:

[0035]

[0036] In a second aspect, an embodiment of the present application further provides a twin-screw compressor, comprising a twin-screw compressor rotor profile as described in any one of the above items.

[0037] Beneficial effects:

[0038] 1. This application adopts a rotor profile design method based on rack line. Compared with the traditional profile design method, the rack line method has the advantages of simple profile design process and high efficiency, and uses an optimization algorithm to optimize the generated rack profile. The optimization algorithm selected here has a mapping function from input to output, which can solve many complex nonlinear problems and can also solve problems where the objective function cannot be expressed in an analytical form. It realizes the optimization of the rack profile and the improvement of the rotor profile, so that the contact line length is relatively small, the leakage triangle area is minimized, the leakage of the compressor is reduced to a large extent, and the relative volumetric efficiency is relatively high.

[0039] 2. This application optimizes the rack so that the female rotor adopts a more appropriate tooth depth radius, which is very suitable for large-flow compressors, while retaining a relatively deep tooth thickness, so that the male rotor achieves better rigidity conditions.

[0040] 3. The profile of the female rotor of the present application is designed to be streamlined, which reduces the disturbance resistance of the airflow, reduces losses, reduces noise, and improves the operating efficiency of the rotor;

[0041] 4. The optimized rotor tooth profile of the present application reduces unnecessary energy losses, such as gas leakage and friction losses. This design enables the compressor to consume less energy to complete the same compression task under the same working conditions.

[0042] 5. The optimized rotor tooth profile of this application takes into account the feasibility of the manufacturing process, so that it can be accurately manufactured using existing processing technology. At the same time, due to the flexibility of the geometric method and genetic algorithm, the tooth profile can be fine-tuned according to different application requirements and working conditions to adapt to different compressor models and working conditions. This adaptability makes the new screw compressor have a wide range of application potential in multiple fields. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For those skilled in the art, other drawings can be obtained based on these drawings without creative work.

[0044] Figure 1 A schematic diagram of the profile of the male and female rotors meshing with each other in an embodiment provided in the present application;

[0045] Figure 2 A schematic diagram of a rack line when the male and female rotors are meshed with each other in an embodiment provided in the present application;

[0046] Figure 3 A schematic diagram of a female rotor tooth curve in an embodiment provided in the present application;

[0047] Figure 4 A schematic diagram of a positive rotor tooth curve in an embodiment provided in the present application;

[0048] Figure 5 A schematic diagram of the profile of the male and female rotors meshing with each other in another embodiment provided in the embodiment of the present application;

[0049] Figure 6 A schematic diagram of a rack line when the male and female rotors are meshed with each other in another embodiment provided in the embodiment of the present application;

[0050] Figure 7 A schematic diagram of a female rotor tooth curve in another embodiment provided in the embodiment of the present application;

[0051] Figure 8 A schematic diagram of a positive rotor tooth curve in another embodiment provided in the present application.

[0052] Reference numerals:

[0053] O is the axis of the rack coordinate system, O1 is the axis of the tooth profile coordinate system of the male rotor, and O2 is the axis of the tooth profile coordinate system of the female rotor;

[0054] R 1j is the male rotor pitch radius;

[0055] R 2j is the pitch radius of the female rotor;

[0056] A is the center distance between the two rotors, A = R 1j +R 2j ;

[0057] L1 is the length of segment AB;

[0058] O3 is the center of segment BC;

[0059] O4 is the center of the CD segment;

[0060] O5 is the center of the DE segment;

[0061] O6 is the center of segment EF;

[0062] O7 is the center of segment FG;

[0063] O8 is the center of the GH segment;

[0064] O9 is the center of the HI segment;

[0065] L2 is the length of the IJ segment. DETAILED DESCRIPTION

[0066] The technical solutions in the embodiments of the present application will be described clearly and completely below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work are within the scope of protection of the present application.

[0067] It should be understood that although the terms first, second, etc. may be used herein to describe various components, these components should not be limited by these terms. These terms are used to distinguish one component from another component. Therefore, the first component discussed below can be referred to as the second component without departing from the teachings of the concepts of the present application. As used herein, the term "and / or" includes any one of the associated listed items and all combinations of one or more.

[0068] Those skilled in the art will appreciate that the drawings are only schematic diagrams of example embodiments and may not be to scale. The modules or processes in the drawings are not necessarily required to implement the present application and therefore cannot be used to limit the scope of protection of the present application.

[0069] The screw compressor uses a pair of screw rotors that rotate in the casing to achieve gas compression and power transmission. With a series of unique advantages such as simple structure, good power balance, energy saving and high efficiency, the screw compressor has become the fastest-growing volumetric compression machinery in recent years, and is widely used in industrial fields such as aerodynamics, refrigeration and air conditioning, petrochemicals, process flow and fuel cells. As the core part of the screw compressor, the screw rotor is required to have a maximum inter-tooth volume, good meshing characteristics and small gas power loss. Among them, the intersection line between the tooth surface of the rotor and the vertical plane of the rotor axis is called the profile. Therefore, the screw rotor profile is usually composed of multiple curves connected, and the profile is complex and asymmetric; its spiral tooth profile also has the characteristics of large pitch, large helix angle and large tooth height, which determines the level of most performance parameters of the compressor.

[0070] The rotor deformation under stress, thermal expansion and meshing characteristics of the rotor profile are studied, and based on this, an efficient rotor profile is designed to improve the working efficiency of the twin-screw compressor. The friction, leakage and heat exchange mechanisms during the operation of the compressor are studied, and the optimization design is carried out for different problems to get rid of the previous empirical design, so as to further improve the relevant performance and parameters. The performance of the twin-screw compressor is mainly reflected by the rack. The rotor profile can be generated by first designing the rack in sections, and then the rack line can be optimized in sections to optimize the profile. This avoids the simultaneous design of the yin and yang rotor profiles, reduces the calculation amount of the optimization design, and improves the design efficiency of the rotor profile. Therefore, based on the above analysis, the rack method and the rotor method can be combined to design a rotor profile with excellent performance and develop a tooth profile through the optimization algorithm, so as to improve the pressure difference that the compressor of the rotor can withstand, increase the area utilization coefficient of the tooth shape and reduce the leakage of the rotor to improve the efficiency of the screw compressor.

[0071] In view of this, the present application provides a twin-screw compressor rotor profile, which adopts a segmented rack curve, optimizes each segment of the tooth curve, obtains the corresponding profile after optimization, and improves the efficiency of the compressor.

[0072] See also Figure 1 , Figure 3 and Figure 4 , Figure 1 This is a schematic diagram of the profile of the male and female rotors meshing with each other in an embodiment provided in the present application. Figure 3 A schematic diagram of a female rotor tooth curve in an embodiment provided in the present application, Figure 4 A schematic diagram of a male rotor tooth curve in an embodiment provided for an embodiment of the present application. The rotor profile of the twin-screw compressor in this embodiment includes a male rotor tooth curve and a female rotor tooth curve, wherein the male rotor tooth curve includes a sequentially smoothly connected A1B1 segment, a B1C1 segment, a C1D1 segment, a D1E1 segment, an E1F1 segment, a F1G1 segment, a G1H1 segment, and a H1I1 segment; and the female rotor tooth curve includes a sequentially smoothly connected A2B2 segment, a B2C2 segment, a C2D2 segment, a D2E2 segment, an E2F2 segment, a F2G2 segment, a G2H2 segment, and a H2I2 segment.

[0073] This embodiment obtains the corresponding optimized profile by segmenting the male rotor tooth curve and the female rotor tooth curve, thereby obtaining the rotor profile of the twin-screw compressor with improved design efficiency.

[0074] In some embodiments, see Figure 2 , Figure 2 A schematic diagram of the rack line when the male and female rotors are meshed with each other in an embodiment provided in the present application. The male rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the male rotor; the female rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the female rotor. The rack line is formed by the meshing of the female rotor and the male rotor, and the rack line includes AB segment, BC segment, CD segment, DE segment, EF segment, FG segment, GH segment and HI segment which are smoothly connected in sequence.

[0075] The rack line where the female rotor and the male rotor mesh with each other is drawn by segmenting the rack and combining one or more combinations of straight line segments, circular arc segments, and elliptical arc segments.

[0076] It should be noted that the positive rotor tooth curve and the negative rotor tooth curve are generated according to the rack line through the coordinate conversion formula, and the coordinate conversion formula is as follows:

[0077]

[0078] In view of this, the performance of the twin-screw compressor can be reflected by the rack. Therefore, the rack line can be obtained by designing the rack in sections, and the rack line can be used to generate the rotor tooth curve. Then, the rotor tooth curve can be optimized in sections to achieve the purpose of optimizing the rotor profile. This avoids the simultaneous design of the yin and yang rotor profiles, reduces the calculation amount of the optimization design, and improves the design efficiency of the rotor profile.

[0079] This embodiment adopts a rotor profile design method based on a rack line. Compared with the traditional profile design method, the rack line method has the advantages of a simple profile design process and high efficiency. The generated rack profile can be optimized using an optimization algorithm. The optimization algorithm selected here has a mapping function from input to output, which can solve many complex nonlinear problems and can also solve problems where the objective function cannot be expressed in an analytical form. The optimization of the rack profile and the improvement of the rotor profile are achieved, so that the contact line length is relatively small, the leakage triangle area is minimized, the leakage of the compressor is reduced to a large extent, and the relative volumetric efficiency is relatively high.

[0080] In some embodiments, see Figure 2 , Figure 2 A schematic diagram of a rack line when the male and female rotors are meshed with each other in an embodiment provided in the present application. The AB segment, BC segment, CD segment, DE segment, EF segment, FG segment, GH segment and HI segment of the rack line are as follows:

[0081] The AB segment is a straight line, and the length of the AB segment L1 is n1 times the radius of the negative rotor pitch circle R 2j (R 2j =R2, that is, L1=n1*R2, R2 is the radius of the tooth top circle of the female rotor), segment AB is smoothly connected to segment HI at the starting point, and segment AB is tangent to segment BC at the end point; n1 is a positive number greater than 0.1 and less than or equal to 0.25.

[0082] The BC segment is an arc with O3 as the center. The radius R3 of the BC segment is n2 times the radius R of the negative rotor pitch circle. 2j (R 2j =R2, that is, R3=n1*R2), segment BC is smoothly connected to segment AB at the starting point, and segment BC is tangent to segment CD at the end point; n2 is a positive number greater than 0.05 and less than or equal to 0.25.

[0083] Segment CD is an elliptical arc centered at O4. The major diameter of segment CD is R 7-1 n3 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-1 =n3*R2), CD segment short diameter R 7-2 n4 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-2 =n4*R2), segment CD is smoothly connected to segment BC at the starting point, and segment CD is tangent to segment DE at the end point; n3 is a positive number greater than 0.4 and less than or equal to 0.6, and n4 is a positive number greater than 0.15 and less than or equal to 0.35.

[0084] The DE segment is an elliptical arc with O5 as the center. The major diameter of the DE segment is R7-3 n5 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-3 =n5*R2), the short diameter of DE section R 7-4 n6 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-4 =n6*R2), segment DE is smoothly connected to segment CD at the starting point, and segment DE is tangent to segment EF at the end point; n5 is a positive number greater than 0.3 and less than or equal to 0.7, and n6 is a positive number greater than 0.1 and less than or equal to 0.3.

[0085] Segment EF is an arc with O6 as the center. The radius R4 of segment EF is n6 times the radius R of the pitch circle of the negative rotor. 2j (R 2j =R2, that is, R4=n6*R2), segment EF is smoothly connected to segment DE at the starting point, and segment EF is tangent to segment FG at the end point; n6 is a positive number greater than 0.6 and less than or equal to 0.9.

[0086] The FG segment is an arc with O7 as the center. The radius R5 of the FG segment is n7 times the radius R of the negative rotor pitch circle. 2j (R 2j =R2, that is, R5=n7*R2), the FG segment is smoothly connected to the EF segment at the starting point, the FG segment is tangent to the GH segment at the end point, and is located on the tangent line of the GH segment; n7 is a positive number greater than 0.5 and less than or equal to 0.8.

[0087] The GH segment is an elliptical arc with O8 as the center. The major diameter of the GH segment is R 7-5 n8 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-5 =n8*R2), GH section short diameter R 7-6 n9 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-6 =n9*R2), segment GH is smoothly connected to segment FG at the starting point, and segment GH is tangent to segment HI at the end point; n8 is a positive number greater than 0.6 and less than or equal to 0.9, and n9 is a positive number greater than 0.2 and less than or equal to 0.5.

[0088] The HI segment is an arc with O9 as the center, and the radius R6 of the HI segment is n 10 Double the pitch radius of the rotor R 2j (R 2j =R2, that is, R6 = n 10*R2), the HI segment is smoothly connected to the GH segment at the starting point, and the HI segment is tangent to the IA segment at the end point; n 10 A positive number greater than 0.3 and less than or equal to 0.5.

[0089] In some embodiments, when the rack line is a sequence of smoothly connected AB segments, BC segments, CD segments, DE segments, EF segments, FG segments, GH segments, and HI segments, the gear ratio of the female rotor to the male rotor is 5:3. It should be noted that the optimized rotor tooth profile of this embodiment takes into account the feasibility of the manufacturing process, so that it can be accurately manufactured by existing processing technology. At the same time, due to the flexibility of the geometric method and the genetic algorithm, the tooth profile can be fine-tuned according to different application requirements (the gear ratio of the female rotor to the male rotor is 5:3 or the gear ratio of the female rotor to the male rotor is 4:3) and working conditions to adapt to different compressor models and working conditions. This adaptability makes the new screw compressor have broad application potential in many fields.

[0090] In some embodiments, see Figure 5 , Figure 7 and Figure 8 , Figure 5 This is a schematic diagram of the profile of the male and female rotors meshing with each other in another embodiment provided in the embodiment of the present application. Figure 7 A schematic diagram of a female rotor tooth curve in another embodiment provided in the present application, Figure 8 A schematic diagram of a male rotor tooth curve in another embodiment provided for the present application. The male rotor tooth curve includes a sequentially smoothly connected A1B1 segment, a B1C1 segment, a C1D1 segment, a D1E1 segment, an E1F1 segment, a F1G1 segment, a G1H1 segment, an H1I1 segment, and an I1J1 segment; the female rotor tooth curve includes a sequentially smoothly connected A2B2 segment, a B2C2 segment, a C2D2 segment, a D2E2 segment, an E2F2 segment, a F2G2 segment, a G2H2 segment, an H2I2 segment, and an I2J2 segment.

[0091] This embodiment uses segmented male rotor tooth curves and female rotor tooth curves, and then optimizes each segment of the male rotor tooth curves and female rotor tooth curves to obtain the corresponding profile after optimization, thereby obtaining the rotor profile of the twin-screw compressor with improved design efficiency. In addition, when designing the rotor profile, the problem of inconvenience in modifying the profile often occurs. This embodiment adds a ninth segment I1J1 on the basis of the eight segments of male rotor tooth curves, and adds a ninth segment I2J2 on the basis of the eight segments of female rotor tooth curves, so as to achieve modification of the profile and solve the problem of inconvenience in modifying the profile when designing the rotor profile.

[0092] In some embodiments, see Figure 6 , Figure 6A schematic diagram of the rack line when the male and female rotors are meshed with each other in another embodiment provided for the present application. The male rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the male rotor; the female rotor tooth curve is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the female rotor. The rack line is formed by the meshing of the female rotor and the male rotor, and the rack line includes AB segment, BC segment, CD segment, DE segment, EF segment, FG segment, GH segment, HI segment and IJ segment which are smoothly connected in sequence.

[0093] The rack line where the female rotor and the male rotor mesh with each other is drawn by segmenting the rack and combining one or more combinations of straight line segments, circular arc segments, and elliptical arc segments.

[0094] It should be noted that the positive rotor tooth curve and the negative rotor tooth curve are generated according to the rack line through the coordinate conversion formula, and the coordinate conversion formula is as follows:

[0095]

[0096] In view of this, the performance of the twin-screw compressor can be reflected by the rack. Therefore, the rack line can be obtained by designing the rack in sections, and the rack line can be used to generate the rotor tooth curve. Then, the rotor tooth curve can be optimized in sections to achieve the purpose of optimizing the rotor profile. This avoids the simultaneous design of the male and female rotor profiles, reduces the amount of calculation for the optimization design, and improves the design efficiency of the rotor profile. In addition, when designing the rotor profile, the problem of inconvenience in modifying the profile often occurs. This embodiment adds a ninth section IJ on the basis of the eight-section rack line, so as to facilitate obtaining the ninth section I1J1 of the male rotor tooth curve and the ninth section I2J2 of the female rotor tooth curve, that is, the modification of the profile is achieved by adding the I1J1 section and the I2J2 section, solving the problem of inconvenience in modifying the profile when designing the rotor profile.

[0097] In some embodiments, see Figure 6 , Figure 6 A schematic diagram of a rack line when the male and female rotors are meshed with each other in another embodiment provided in the present application. The AB segment, BC segment, CD segment, DE segment, EF segment, FG segment, GH segment, HI segment and IJ segment of the rack line are as follows:

[0098] The AB segment is a straight line, and the length of the AB segment L1 is n1 times the radius of the negative rotor pitch circle R 2j (R 2j =R2, that is, L1=n1*R2), segment AB is smoothly connected to segment IJ at the starting point, and segment AB is tangent to segment BC at the end point; n1 is a positive number greater than 0.1 and less than or equal to 0.25.

[0099] The BC segment is an arc with O3 as the center. The radius R3 of the BC segment is n2 times the radius R of the negative rotor pitch circle. 2j (R2j =R2, that is, R3=n1*R2), segment BC is smoothly connected to segment AB at the starting point, and segment BC is tangent to segment CD at the end point; n2 is a positive number greater than 0.05 and less than or equal to 0.25.

[0100] Segment CD is an elliptical arc centered at O4. The major diameter of segment CD is R 7-1 n3 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-1 =n3*R2), CD segment short diameter R 7-2 n4 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-2 =n4*R2), segment CD is smoothly connected to segment BC at the starting point, and segment CD is tangent to segment DE at the end point; n3 is a positive number greater than 0.4 and less than or equal to 0.6, and n4 is a positive number greater than 0.15 and less than or equal to 0.35.

[0101] The DE segment is an elliptical arc with O5 as the center. The major diameter of the DE segment is R 7-3 n5 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-3 =n5*R2), the short diameter of DE section R 7-4 n6 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-4 =n6*R2), segment DE is smoothly connected to segment CD at the starting point, and segment DE is tangent to segment EF at the end point; n5 is a positive number greater than 0.3 and less than or equal to 0.7, and n6 is a positive number greater than 0.1 and less than or equal to 0.3.

[0102] Segment EF is an arc with O6 as the center. The radius R4 of segment EF is n6 times the radius R of the pitch circle of the negative rotor. 2j (R 2j =R2, that is, R4=n6*R2), segment EF is smoothly connected to segment DE at the starting point, and segment EF is tangent to segment FG at the end point; n6 is a positive number greater than 0.6 and less than or equal to 0.9.

[0103] The FG segment is an arc with O7 as the center. The radius R5 of the FG segment is n7 times the radius R of the negative rotor pitch circle. 2j (R 2j =R2, that is, R5=n7*R2), the FG segment is smoothly connected to the EF segment at the starting point, the FG segment is tangent to the GH segment at the end point, and is located on the tangent line of the GH segment; n7 is a positive number greater than 0.5 and less than or equal to 0.8.

[0104] The GH segment is an elliptical arc with O8 as the center. The major diameter of the GH segment is R 7-5 n8 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-5 =n8*R2), GH section short diameter R 7-6 n9 times the negative rotor pitch radius R 2j (R 2j =R2, that is, R 7-6 =n9*R2), segment GH is smoothly connected to segment FG at the starting point, and segment GH is tangent to segment HI at the end point; n8 is a positive number greater than 0.6 and less than or equal to 0.9, and n9 is a positive number greater than 0.2 and less than or equal to 0.5.

[0105] The HI segment is an arc with O9 as the center, and the radius R6 of the HI segment is n 10 times the rotor pitch radius (R 2j =R2, that is, R6 = n 10 *R2), the HI segment is smoothly connected to the GH segment at the starting point, and the HI segment is tangent to the IJ segment at the end point; n 10 A positive number greater than 0.3 and less than or equal to 0.5.

[0106] The IJ segment is a straight line, and the length of the IJ segment L2 is n 11 Double the pitch radius of the rotor R 2j (R 2j =R2, that is, L2 = n 11 *R2), the IJ segment is smoothly connected to the HI segment at the starting point, and the IJ segment is tangent to the JA segment at the end point, n 11 A positive number greater than 0.05 and less than or equal to 0.2.

[0107] In view of this, this embodiment adds a straight rack line IJ segment so that the yin and yang rotors change from 3 / 5 teeth to 3 / 4 teeth. The tooth profile series of the male and female rotors of the screw compressor are formed with different sizes of center distances, and the tooth curves of two adjacent segments have a common tangent at the connection point.

[0108] In some embodiments, when the rack line is a smoothly connected AB segment, BC segment, CD segment, DE segment, EF segment, FG segment, GH segment, HI segment and IJ segment in sequence, the gear ratio of the female rotor to the male rotor is 4: 3. It should be noted that the gear ratio of the female rotor to the male rotor is 4: 3, which further increases the gas volume of the compressor, is suitable for the working conditions of low pressure ratio and large flow rate, and reduces the machining time cycle of the rotor.

[0109] Correspondingly, an embodiment of the present application also provides a twin-screw compressor, which includes the twin-screw compressor rotor profile in any of the above embodiments. The twin-screw compressor can achieve optimal meshing between the male rotor and the female rotor during operation, the two adjacent segments of the tooth curve have a smooth transition at the connection point, the rotor area utilization coefficient is relatively large, the contact line is short and the leakage triangle is relatively small, the profile is streamlined, and the male and female rotors are the same size, and have good compressor thermodynamic properties, thereby improving the working efficiency of the screw compressor, and improving the accuracy during the processing process, and extending the life of the tool. Since the twin-screw compressor rotor profile is described in detail above, it will not be repeated here.

[0110] In the above embodiments, the description of each embodiment has its own emphasis. For parts that are not described in detail in a certain embodiment, reference can be made to the relevant descriptions of other embodiments.

[0111] The twin-screw compressor rotor profile provided in the embodiments of the present application is introduced in detail above, and the principles and implementation methods of the present application are explained by using specific examples. The description of the above embodiments is only used to help understand the technical solution and its core idea of ​​the present application; ordinary technicians in this field should understand that: they can still modify the technical solutions recorded in the aforementioned embodiments, or replace some of the technical features therein with equivalents; and these modifications or replacements do not make the essence of the corresponding technical solution deviate from the scope of the technical solution of the embodiments of the present application.

Claims

1. A twin-screw compressor rotor profile, characterized in that: It includes the positive rotor tooth curve and the negative rotor tooth curve, where: The male rotor tooth curve includes a sequence of smoothly connected A1B1 segment, B1C1 segment, C1D1 segment, D1E1 segment, E1F1 segment, F1G1 segment, G1H1 segment and H1I1 segment; The female rotor tooth curve includes a segment A2B2, a segment B2C2, a segment C2D2, a segment D2E2, a segment E2F2, a segment F2G2, a segment G2H2 and a segment H2I2 which are smoothly connected in sequence.

2. The twin-screw compressor rotor profile according to claim 1, characterized in that: The tooth curve of the male rotor is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the male rotor; the tooth curve of the female rotor is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the female rotor; The rack line is formed by the meshing of the female rotor and the male rotor, and the rack line includes an AB segment, a BC segment, a CD segment, a DE segment, an EF segment, a FG segment, a GH segment and a HI segment which are smoothly connected in sequence.

3. The twin-screw compressor rotor profile according to claim 2, characterized in that: In the rack line: Segment AB is a straight line, the length of which is n1 times the pitch radius of the negative rotor. Segment AB is smoothly connected to segment HI at the starting point, and segment AB is tangent to segment BC at the end point; n1 is a positive number greater than 0.1 and less than or equal to 0.25; Segment BC is an arc, and its radius is n2 times the pitch radius of the female rotor. Segment BC is smoothly connected to segment AB at the starting point, and segment BC is tangent to segment CD at the end point; n2 is a positive number greater than 0.05 and less than or equal to 0.25; The CD segment is an elliptical arc, the major diameter of which is n3 times the pitch radius of the female rotor, and the minor diameter is n4 times the pitch radius of the female rotor. The CD segment is smoothly connected to the BC segment at the starting point, and the CD segment is tangent to the DE segment at the end point; n3 is a positive number greater than 0.4 and less than or equal to 0.6, and n4 is a positive number greater than 0.15 and less than or equal to 0.35; The DE segment is an elliptical arc, the major diameter of which is n5 times the pitch radius of the female rotor, and the minor diameter is n6 times the pitch radius of the female rotor. The DE segment is smoothly connected to the CD segment at the starting point, and the DE segment is tangent to the EF segment at the end point; n5 is a positive number greater than 0.3 and less than or equal to 0.7, and n6 is a positive number greater than 0.1 and less than or equal to 0.3; Segment EF is an arc, and its radius is n6 times the pitch radius of the female rotor. Segment EF is smoothly connected to segment DE at the starting point, and segment EF is tangent to segment FG at the end point; n6 is a positive number greater than 0.6 and less than or equal to 0.9; The FG segment is an arc, and its radius is n7 times the pitch radius of the female rotor. The FG segment is smoothly connected to the EF segment at the starting point, and is tangent to the GH segment at the end point and is located on the tangent line of the GH segment. n7 is a positive number greater than 0.5 and less than or equal to 0.

8. The GH segment is an elliptical arc, the major diameter of which is n8 times the pitch radius of the female rotor, and the minor diameter is n9 times the pitch radius of the female rotor. The GH segment is smoothly connected to the FG segment at the starting point, and the GH segment is tangent to the HI segment at the end point; n8 is a positive number greater than 0.6 and less than or equal to 0.9, and n9 is a positive number greater than 0.2 and less than or equal to 0.5; Segment HI is an arc with a radius of n. 10 times the pitch radius of the negative rotor, the HI segment is smoothly connected to the GH segment at the starting point, and the HI segment is tangent to the IA segment at the end point; n 10 A positive number greater than 0.3 and less than or equal to 0.

5.

4. The twin-screw compressor rotor profile according to claim 3, characterized in that: The gear ratio of the female rotor to the male rotor is 5:

3.

5. The twin-screw compressor rotor profile according to claim 1, characterized in that: The positive rotor tooth curve further includes an I1J1 segment, and the negative rotor tooth curve further includes an I2J2 segment.

6. The twin-screw compressor rotor profile according to claim 5, characterized in that: The tooth curve of the male rotor is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the male rotor; the tooth curve of the female rotor is obtained by converting the rack line from the rack coordinate system to the tooth profile coordinate system of the female rotor; The rack line is formed by the meshing of the female rotor and the male rotor, and the rack line includes an AB segment, a BC segment, a CD segment, a DE segment, an EF segment, a FG segment, a GH segment, a HI segment, and an IJ segment which are smoothly connected in sequence.

7. The twin-screw compressor rotor profile according to claim 6, characterized in that: In the rack line: Segment AB is a straight line, the length of which is n1 times the pitch radius of the negative rotor. Segment AB is smoothly connected to segment IJ at the starting point, and segment AB is tangent to segment BC at the end point; n1 is a positive number greater than 0.1 and less than or equal to 0.25; Segment BC is an arc, and its radius is n2 times the pitch radius of the female rotor. Segment BC is smoothly connected to segment AB at the starting point, and segment BC is tangent to segment CD at the end point; n2 is a positive number greater than 0.05 and less than or equal to 0.25; The CD segment is an elliptical arc, the major diameter of which is n3 times the pitch radius of the female rotor, and the minor diameter is n4 times the pitch radius of the female rotor. The CD segment is smoothly connected to the BC segment at the starting point, and the CD segment is tangent to the DE segment at the end point; n3 is a positive number greater than 0.4 and less than or equal to 0.6, and n4 is a positive number greater than 0.15 and less than or equal to 0.35; The DE segment is an elliptical arc, the major diameter of which is n5 times the pitch radius of the female rotor, and the minor diameter is n6 times the pitch radius of the female rotor. The DE segment is smoothly connected to the CD segment at the starting point, and the DE segment is tangent to the EF segment at the end point; n5 is a positive number greater than 0.3 and less than or equal to 0.7, and n6 is a positive number greater than 0.1 and less than or equal to 0.3; Segment EF is an arc, and its radius is n6 times the pitch radius of the female rotor. Segment EF is smoothly connected to segment DE at the starting point, and segment EF is tangent to segment FG at the end point; n6 is a positive number greater than 0.6 and less than or equal to 0.9; The FG segment is an arc, and its radius is n7 times the pitch radius of the female rotor. The FG segment is smoothly connected to the EF segment at the starting point, and is tangent to the GH segment at the end point. n7 is a positive number greater than 0.5 and less than or equal to 0.8; The GH segment is an elliptical arc, the major diameter of which is n8 times the pitch radius of the female rotor, and the minor diameter is n9 times the pitch radius of the female rotor. The GH segment is smoothly connected to the FG segment at the starting point, and the GH segment is tangent to the HI segment at the end point; n8 is a positive number greater than 0.6 and less than or equal to 0.9, and n9 is a positive number greater than 0.2 and less than or equal to 0.5; Segment HI is an arc with a radius of n. 10 times the pitch radius of the negative rotor, the HI segment is smoothly connected to the GH segment at the starting point, and the HI segment is tangent to the IJ segment at the end point and is located on the tangent line of the IJ segment; n 10 is a positive number greater than 0.3 and less than or equal to 0.5; Segment IJ is a straight line, and its length is n 11 times the pitch radius of the negative rotor, the IJ segment is smoothly connected to the HI segment at the starting point, and the IJ segment is tangent to the JA segment at the end point, n 11 A positive number greater than 0.05 and less than or equal to 0.

2.

8. The twin-screw compressor rotor profile according to claim 7, characterized in that: The gear ratio of the female rotor to the male rotor is 4:

3.

9. The twin-screw compressor rotor profile according to claim 2, characterized in that: The positive rotor tooth curve and the negative rotor tooth curve are generated according to the rack line by using a coordinate conversion formula, and the coordinate conversion formula is specifically as follows:

10. A twin-screw compressor, characterized in that: A twin-screw compressor rotor profile comprising any one of claims 1 to 9.

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