Conical modified intermeshing twin screw rotor structure and design method thereof

Abstract

The application discloses a kind of conical modified line internal meshing double screw rotor structure and its design method, including outer rotor and the inner rotor being arranged in outer rotor and being meshed with it, the curve segment A2B2 of outer rotor profile is circular arc segment, the curve segment A1B1C1 of inner rotor profile is the envelope segment of curve segment A2B2, the curve segment B2C2 of outer rotor profile is the envelope segment of curve segment B1C1, the curve segment C1D1 of inner rotor profile is about axis O1C1 symmetry with curve segment A1B1C1, the curve segment C2D2 of outer rotor profile is about axis O2C2 symmetry with curve segment A2B2C2;With outer rotor single tooth profile of inner rotor being rotated and spliced in sequence can be formed into complete multi-tooth inner rotor profile, adjust the distance of the generating center of circular arc segment and the center of outer rotor profile or the radius of circular arc segment, realize the adjustment of inner rotor profile shape.The application can realize the regulation of internal gas compression process of internal meshing double screw compressor, and ensure rotor thickness.

Description

Technical Field

[0001] This invention belongs to the field of compressors, specifically relating to a conical modified in-line meshing twin-screw rotor structure and its design method. Background Technology

[0002] Compared to traditional twin-screw compressors, internal meshing screw compressors feature a compact structure, low sliding speed in the transmission contact area, large discharge port connection area, and a leak-free triangular shape. Furthermore, they inherit the reliable operation, absence of easily damaged parts like valves, compatibility with liquids, and high operating efficiency of traditional screw compressors. They hold great potential as the next generation of screw compressor rotor structures and can be widely applied in industries such as refrigeration, compressed gases, and chemical and pharmaceutical manufacturing.

[0003] Similar to traditional externally meshing twin-screw compressors, internally meshing screw compressors can be designed with variable pitch to control the compression process of the internal gas, thereby obtaining better thermodynamic performance. However, variable pitch design often results in a smaller exhaust pitch, which leads to thinner exhaust side teeth of the internally meshing screw rotor, resulting in a decrease in its sealing performance, transmission performance and machining performance. Summary of the Invention

[0004] The purpose of this invention is to address the problems in the prior art by providing a conical modified internal meshing twin-screw rotor structure and its design method. This rotor structure can realize the internal compression process of an internal meshing twin-screw compressor under constant pitch conditions, thereby achieving regulation of the internal gas compression process while ensuring rotor tooth thickness, thus obtaining better thermodynamic characteristics.

[0005] To achieve the above objectives, the present invention provides the following technical solution:

[0006] A conical profile internal meshing twin-screw rotor structure includes an outer rotor and an inner rotor disposed inside and meshing with the outer rotor. The outer rotor profile curve segment A2B2 is an arc segment, the inner rotor profile curve segment A1B1C1 is the envelope segment of curve segment A2B2, the outer rotor profile curve segment B2C2 is the envelope segment of curve segment B1C1, the inner rotor profile curve segment C1D1 is symmetrical to curve segment A1B1C1 about axis O1C1, where O1 is the center of the outer rotor profile, and the outer rotor profile curve segment C2D2 is symmetrical to curve segment A2B2C2 about axis O2C2, where O2 is the center of the outer rotor profile. The outer rotor single-tooth profile A2B2C2D2 is composed of curve segments A2B2, B2C2, and C2D2; the inner rotor single-tooth profile A1B1C1D1 is composed of curve segments A1B1C1 and C1D1. The inner rotor single-tooth profile A1B1C1D1 is rotated sequentially by an angle of 2π / N and spliced ​​into N segments to form a complete multi-tooth inner rotor profile. The outer rotor single-tooth profile A2B2C2D2 is rotated sequentially by an angle of 2π / (N+1) and spliced ​​into N+1 segments to form a complete multi-tooth outer rotor profile. Here, N represents the number of teeth in the inner rotor profile. The generation center O of the arc segment is adjusted... e Distance O from the center O2 of the outer rotor profile e The radius r of O2 or the arc segment is used to adjust the shape of the inner and outer rotor profiles.

[0007] Preferably, the pitch circle radii of the inner and outer rotor profiles are r and r, respectively. p1 With r p2 It conforms to the following relationship:

[0008]

[0009] In the formula, N and N+1 are the number of teeth of the inner and outer rotors, respectively, and d is the center distance between the inner and outer rotor profiles.

[0010] Preferably, in the coordinate system O2xy, the arc parameter expression of the curve segment A2B2 of the outer rotor profile is as follows:

[0011]

[0012] In the formula, O1O e The center O of the generated arc segment e The distance from the center O1 of the inner rotor profile, θ is the angular parameter, and α represents the range of values ​​for the angular parameter.

[0013] Preferably, in the coordinate system O1xy, the curve segment A1B1C1 of the inner rotor profile is obtained by the following calculation expression:

[0014]

[0015] In the formula, M i1With M i2 Let each represent a rotation matrix, which is derived from the following equation:

[0016]

[0017] In the formula, ξ represents the rotation angle parameter variable, which is an intermediate parameter. Its relationship with the angle parameter θ is determined by the following relationship:

[0018]

[0019] The range of values ​​for the angular parameter variable α is determined by the following formula:

[0020]

[0021] Preferably, in the coordinate system O2xy, the calculation expression for the curve segment B2C2 of the outer rotor profile is as follows:

[0022]

[0023] In the formula, M i1 With M i2 Let ξ be the expression for the rotation angle parameter variable. The relationship between parameter variable ξ and the angular parameter θ representing curve segment B1C1 conforms to the following expression:

[0024]

[0025] Preferably, the relationship between the outer diameter of the outer rotor profile and the center distance is as follows:

[0026] R2=O1O e -r+2d

[0027] In the formula, O1O e The inner rotor profile center O1 and the generating circle center O of the arc segment e The distance between the inner and outer rotor profiles is d, where d is the center distance between the inner and outer rotor profiles.

[0028] Preferably, the axial position of the outer rotor and the tooth tip radius of the corresponding profile conform to the following relationship:

[0029]

[0030] In the formula, For the corner The initial tooth tip radius of the outer rotor profile is R2(0), where R2(0) is the initial tooth tip radius of the outer rotor profile. For the corner The corresponding rotor axial position and rotation angle This represents the rotation angle of the rotor profile along the rotor's central axis, where α is the cone angle of the outer rotor;

[0031] The rotor profiles at different axial positions have the same center distance, and the relationship between the rotor axial position and the rotor angle conforms to the following expression:

[0032]

[0033] In the formula, Indicates rotor rotation angle The corresponding pitch.

[0034] Preferably, the radius of the generating circle of the outer rotor arc segment at different rotor axial positions is... The following relationship must be satisfied:

[0035]

[0036] In the formula, r(0) is the radius of the generated circle of the outer rotor arc segment at the initial axial position of the rotor.

[0037] Preferably, the distance between the center of the arc and the center of the outer rotor profile at different rotor axial positions is: The following relationship must be satisfied:

[0038]

[0039] In the formula, O1O e (0) is the distance between the center of the arc at the initial axial position of the rotor and the center of the inner rotor profile.

[0040] A design method for the conical modified in-line meshing twin-screw rotor structure includes the following steps:

[0041] Based on the exhaust volume requirements, determine the center distance d between the inner and outer rotor profiles and the initial tooth tip radius R2(0) of the outer rotor profile;

[0042] Based on sealing requirements and intake / exhaust conditions, determine the number of teeth N in the inner rotor profile and the rotor angle. Corresponding pitch And the cone angle α of the outer rotor, determine the tooth tip radius of the outer rotor profile at different rotor axial positions. In the formula For the corner The rotor axial position corresponding to the time is calculated using the following formula:

[0043] Based on the determined parameters, the rotor profile corresponding to different rotor axial positions is generated by generating circles;

[0044] By adjusting the center O of the generated arc segment of the profile e Distance O from the center O2 of the outer rotor profile e The radius r of the O2 or the arc segment of the profile is used to adjust the shape of the inner and outer rotor profiles.

[0045] Compared with the prior art, the present invention has at least the following beneficial effects:

[0046] This rotor structure enables the internal compression process of an internally meshing twin-screw compressor under constant pitch conditions. While controlling the compression process of the gas inside the compressor, it also ensures the rotor tooth thickness, thereby achieving superior thermodynamic characteristics. Specifically, it employs inner and outer rotor profiles generated based on circular arcs, with rotor profiles of different outer diameters at different rotor axial positions. This achieves a gradually decreasing gas space along the rotor axially from the intake section to the exhaust end, thus enabling the internal compression process of the gas while maintaining a certain rotor pitch. Ultimately, this results in excellent sealing and transmission performance on both the intake and exhaust sides of the rotor. The conical variable profile internally meshing twin-screw rotor structure of this invention offers flexible design, allowing for optimized adjustment of the location distribution, geometry, and flow conditions of the leakage channels in the working chamber during gas transport, thereby obtaining the optimal rotor geometry to meet different requirements. Attached Figure Description

[0047] Figure 1 A schematic diagram of the profile of the internally meshing twin-screw rotor structure according to an embodiment of the present invention;

[0048] Figure 2 A schematic diagram of the conical helix characterizing the rotor structure in an embodiment of the present invention;

[0049] Figure 3 A schematic diagram of the conical rotor structure generated by the variable profile generating circle radius in an embodiment of the present invention;

[0050] Figure 4 A schematic diagram of the conical rotor structure generated by varying the distance between the center of the circular arc and the center of the outer rotor profile in an embodiment of the present invention;

[0051] Figure 5 The conical rotor structure formed by the two outer diameter control methods in the embodiments of the present invention:

[0052] (a) Transform into the distance between the centers of the circle; (b) Transform into the radius of the circle. Detailed Implementation

[0053] The present invention will now be described in further detail with reference to the accompanying drawings.

[0054] In this embodiment of the invention, the conical profile internal meshing twin-screw rotor structure uses profiles generated by generating circles. Specifically, the outer rotor profile curve segment A2B2 is set as an arc segment, the inner rotor profile curve segment A1B1C1 is set as the envelope segment of curve segment A2B2, and the outer rotor profile curve segment B2C2 is set as the envelope segment of inner rotor profile curve segment B1C1. The inner rotor profile curve segment C1D1 is symmetrical to curve segment A1B1C1 about axis O1C1, and the outer rotor profile curve segment C2D2 is symmetrical to curve segment A2B2C2 about axis O2C2. By rotating the single-tooth profile A1B1C1D1 of the inner rotor sequentially by an angle of 2π / N and splicing N segments, a complete multi-tooth inner rotor profile can be formed. Similarly, by rotating the single-tooth profile A2B2C2D2 of the outer rotor sequentially by an angle of 2π / (N+1) and splicing N+1 segments, a complete multi-tooth outer rotor profile can be formed. Here, N represents the number of teeth in the inner rotor profile. The center O of the arc segment generation can be adjusted. e Distance O from the center O2 of the outer rotor profile e The radius r of O2 or the arc segment is used to adjust the shape of the inner and outer rotor profiles.

[0055] like Figures 2 to 5 As shown, the conical profile internal meshing twin-screw rotor structure of this invention, by setting rotor profiles with different outer diameters at different rotor axial positions and maintaining an appropriate pitch at different axial positions, can form an inner and outer rotor structure with varying working cavity volume along the axial direction. The variation law of the outer rotor pitch and the variation law of the outer rotor profile radius with the rotor axial position can be obtained from... Figure 2 The conical helix is ​​shown. This is achieved by changing the distance O between the center of the generating circle and the center of the rotor profile. e The rotor structure formed by changing the outer diameter of the profile using O2 is as follows: Figure 3 and Figure 5 As shown in Figure (a), the rotor structure formed by changing the outer diameter of the profile by changing the radius r of the arc segment is as follows. Figure 4 and Figure 5 As shown in Figure (b).

[0056] exist Figure 1 In the diagram, the center distance between the inner and outer rotor profiles is d, the number of teeth on the inner and outer rotors are N and N+1 respectively, the radius of the outer rotor generating circle is r, and the distance between the center of the arc and the center of the outer rotor profile is O1O. e .

[0057] The pitch circle radii of the inner and outer rotors are respectively r p1 With r p2 It can be derived from the following formula:

[0058]

[0059] In coordinate system O2xy, the circular arc segment A2B2 of the outer rotor profile is obtained by the following formula:

[0060]

[0061] In the formula, θ represents the angular parameter, and α represents the range of values ​​for the angular parameter.

[0062] In coordinate system O1xy, the envelope A1B1C1 of the inner rotor profile is obtained by the following formula:

[0063]

[0064] In the formula, M i1 With M i2 Let each represent a rotation matrix, and the calculation expression is as follows:

[0065]

[0066] In the formula, ξ represents the rotation angle parameter variable, which is an intermediate parameter. Its relationship with the angle parameter θ is determined by the following relationship:

[0067]

[0068] The range of values ​​for the angular parameter variable α is determined by the following formula:

[0069]

[0070] In coordinate system O2xy, the curve segment B2C2 of the outer rotor profile is obtained by solving for the envelope segment of the curve segment B1C1 of the inner rotor profile:

[0071]

[0072] In the formula, M i1 With M i2 The expression for the rotation angle parameter variable ξ is given. The relationship between the parameter variable ξ and the angle parameter θ representing the profile curve segment B1C1 is obtained by the following formula:

[0073]

[0074] The inner rotor profile curve segment C1D1 is obtained by symmetrically aligning curve segment A1B1C1 with respect to axis O1C1. The outer rotor profile curve segment C2D is obtained by symmetrically aligning curve segment A2B2C2 with respect to axis O2C2. Rotating the single tooth profile A1B1C1D1 of the inner rotor by 2π / N results in a complete multi-tooth inner rotor profile. Rotating the single tooth profile A2B2C2D2 of the outer rotor by 2π / (N+1) results in a complete multi-tooth outer rotor profile. The relationship between the outer diameter and center distance of the rotor profile obtained through the above methods is as follows:

[0075] R2=O1O e -r+2d

[0076] exist Figure 2 In the middle, the cone angle of the outer rotor structure is α, and its rotor axial position and the tooth tip radius of the corresponding profile are:

[0077]

[0078] In the formula, For the corner The tooth tip radius of the outer rotor profile at that time. For the corner The corresponding rotor axial position and rotation angle This indicates the rotation angle of the rotor profile along the rotor's central axis.

[0079] The rotor profiles at different axial positions have the same center distance. The relationship between the rotor axial position and the rotor angle can be calculated by the following formula:

[0080]

[0081] In the formula, Indicates rotor rotation angle The corresponding local pitch.

[0082] exist Figure 3 In this process, the radius of the outer rotor circle generated at different rotor axial positions is controlled to be... This allows for changes in the rotor profile's outer diameter. To achieve a tapered rotor structure, the following relationship must be satisfied:

[0083]

[0084] exist Figure 4 In this process, the distance between the center of the arc and the center of the outer rotor profile at different rotor axial positions is controlled to be O1O. e Similarly, the outer diameter of the rotor profile can be changed. In order for the rotor structure to be conical, the following relationship must be satisfied:

[0085]

[0086] like Figure 5 (a) and Figure 5 As shown in (b), the rotor structure can be flexibly adjusted by reasonably adjusting the cone angle and the variable pitch law of the rotor structure.

[0087] Another embodiment of the present invention also proposes a design method for the aforementioned conical modified in-line meshing twin-screw rotor structure.

[0088] See Figures 1 to 5In (a) and (b), the internal meshing screw rotor proposed in the embodiments of the present invention has a conical structure and rotor profiles with different outer diameters at different rotor axial positions. The rotation angle variation law of the rotor profile along the central axis at different axial positions, i.e., the variable pitch law, is given by the defined conical helix. The shape of the rotor profile can be controlled by adjusting the radius of the outer rotor generating circle or the distance between the center of the arc and the center of the outer rotor profile at different axial positions.

[0089] The specific design process is as follows:

[0090] Based on the exhaust volume requirements, determine the center distance d between the inner and outer rotor profiles and the initial tooth tip radius R2(0) of the outer rotor profile;

[0091] Based on sealing requirements and intake / exhaust conditions, determine the number of teeth N in the inner rotor profile and the rotor angle. Corresponding pitch And the cone angle α of the outer rotor, determine the tooth tip radius of the outer rotor profile at different rotor axial positions. In the formula For the corner The rotor axial position corresponding to the time is calculated using the following formula:

[0092] The rotor profiles corresponding to different rotor axial positions are generated using a circular generation method. Specifically, the outer rotor profile curve segment A2B2 is set as an arc segment, the inner rotor profile curve segment A1B1C1 is set as the envelope of curve segment A2B2, and the outer rotor profile curve segment B2C2 is the envelope of inner rotor profile curve segment B1C1. The inner rotor profile curve segment C1D1 is symmetrical to curve segment A1B1C1 about axis O1C1, and the outer rotor profile curve segment C2D2 is symmetrical to curve segment A2B2C2 about axis O2C2. By rotating the inner rotor single-tooth profile A1B1C1D1 sequentially by 2π / N and splicing N curve segments, a complete multi-tooth inner rotor profile can be formed. Similarly, by rotating the outer rotor single-tooth profile A2B2C2D2 sequentially by 2π / (N+1) and splicing N+1 curve segments, a complete multi-tooth outer rotor profile can be formed. This is achieved by adjusting the arc center O. e The distance from the center O2 of the outer rotor profile or the radius r of the arc segment allows for flexible adjustment of the inner and outer rotor profile shapes. Specifically, the inner and outer rotor pitch circle radii are r and r', respectively. p1 With r p2 It can be derived from the following formula:

[0093]

[0094] In coordinate system O2xy, the circular arc segment A2B2 of the outer rotor profile is represented by the following formula:

[0095]

[0096] In the formula, θ represents the angular parameter, and α represents the range of values ​​for the angular parameter.

[0097] In coordinate system O1xy, the envelope segment A1B1C1 of the circular arc segment A2B2 of the inner rotor profile is obtained by the following formula:

[0098]

[0099] In the formula, M i1 With M i2 Let each represent a rotation matrix, given by the following equation:

[0100]

[0101] In the formula, ξ represents the rotation angle parameter variable, and its relationship with the angle parameter θ is determined by the following relationship:

[0102]

[0103] The range of values ​​for the angular parameter variable α is determined by the following formula:

[0104]

[0105] In coordinate system O2xy, the curve segment B2C2 of the outer rotor profile is obtained by solving for the envelope segment of the curve segment B1C1 of the inner rotor profile:

[0106]

[0107] In the formula, M i1 With M i2 The expression for the rotation angle parameter variable ξ is given by the following formula, which describes the relationship between the parameter variable ξ and the angle parameter θ representing the profile curve segment B1C1:

[0108]

[0109] The relationship between the rotor profile outer diameter and the center distance obtained through the above method is as follows:

[0110] R2=O1O e -r+2d

[0111] By controlling the radius of the circle generated by the outer rotor at different axial positions, Or control the distance between the center of the arc and the center of the outer rotor profile at different axial positions to O1O e This allows for flexible adjustment of the rotor profile outer diameter. To ensure the rotor's axial structure is tapered, one of the following relationships must be satisfied:

[0112]

[0113]

[0114] The rotor structure obtained through the above design can ensure that the gas has a good working chamber leakage channel location distribution, geometry and flow conditions during transportation and compression. By reasonably setting the design parameters, the optimal rotor geometry can be obtained to meet different requirements.

[0115] The conical variable-profile internal meshing twin-screw rotor structure and its design method of this invention, by reasonably defining the rotor cone angle, center distance, initial tooth tip radius, number of rotor teeth, rotor pitch variation law, and rotor profile tooth tip radius variation mode, can achieve flexible adjustment of the variable-pitch variable-profile conical internal meshing twin-screw rotor structure. This allows for flexible adjustment of the working chamber volume variation law, thereby optimizing the location distribution, geometry, and flow conditions of the working chamber leakage channels during gas transport, and ultimately obtaining the optimal rotor geometry to meet different needs. Compared with existing technologies, the rotor structure proposed in this invention can realize the internal compression process of an internally meshing twin-screw compressor under constant pitch or slightly variable pitch conditions. While controlling the internal gas compression process, it ensures rotor tooth thickness, thereby obtaining better thermodynamic characteristics. The structure can be flexibly adjusted, thus achieving optimal rotor geometry control to meet different needs.

[0116] The above-described embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this application, and should all be included within the protection scope of this application.

Claims

1. A conical modified inline meshing twin-screw rotor structure, characterized in that, Includes an outer rotor and an inner rotor disposed inside and meshing with it, and the curved section of the outer rotor profile. A 2 B 2 represents the arc segment, the curved segment of the inner rotor profile. A 1 B 1 C 1 is a curve segment A 2 B The envelope segment of 2, the curved segment of the outer rotor profile. B 2 C 2 is a curve segment B 1 C The envelope segment of 1, the curved segment of the inner rotor profile. C 1 D 1 and curve segment A 1 B 1 C 1. About the shaft O 1 C 1. Symmetry O 1 represents the center of the outer rotor profile, and the curved segment of the outer rotor profile. C 2 D 2 and the curve segment A 2 B 2 C 2. About the shaft O 2 C 2. Symmetrical O 2 is the center of the outer rotor profile; formed by the curved segment A 2 B 2. Curved segment B 2 C 2. Curved segment C 2 D 2. Composition of the outer rotor single tooth profile A 2 B 2 C 2 D 2. From the curve segment A 1 B 1 C 1. Curved segment C 1 D 1. Composition of the inner rotor single tooth profile A 1 B 1 C 1 D 1; The single tooth profile of the inner rotor A 1 B 1 C 1 D 1. Rotate 2π / sequentially N Angle and splicing N The segments form a complete multi-tooth inner rotor profile, while the outer rotor has a single tooth profile. A 2 B 2 C 2 D 2. Rotate sequentially by 2π / ( N +1) Angle and splicing N +1 segment, forming a complete multi-tooth external rotor profile, in which... N Indicates the number of teeth on the inner rotor profile; by adjusting the center of the generated arc segment. O e Center of outer rotor profile O Distance of 2 O e O 2 or the radius of the arc segment r This allows for the adjustment of the inner and outer rotor profile shapes; In coordinate system O 2 xy In the middle, the curved section of the outer rotor profile A 2 B The expression for the arc parameter of 2 is as follows: In the formula, O 1 O e The center of the generated arc segment O e Center of inner rotor profile O A distance of 1 θ For angular parameters, α A variable representing the range of values ​​for the angular parameter; The conical profiled inner meshing twin-screw rotor structure is determined by the exhaust volume requirements, which dictate the center distance between the inner and outer rotor profiles. d and the initial tooth tip radius of the outer rotor profile R 2(0); The number of teeth on the inner rotor profile is determined based on sealing performance and intake / exhaust requirements. N Rotor angle φ Corresponding pitch P ( φ and the cone angle of the outer rotor α Determine the tooth tip radius of the outer rotor profile at different rotor axial positions. In the formula L ( φ ( ) is the turning angle φ The rotor axial position corresponding to the time is calculated using the following formula: ; Based on the determined parameters, the rotor profile corresponding to different rotor axial positions is generated by generating circles; By adjusting the center of the generated arc segment of the profile O e Center of outer rotor profile O Distance of 2 O e O 2 or the radius of the circular arc segment of the profile. r This allows for the adjustment of the inner and outer rotor profile shapes.

2. The conical modified in-line meshing twin-screw rotor structure according to claim 1, characterized in that, The pitch circle radii of the inner and outer rotor profiles are respectively r p1 and r p2 It conforms to the following relationship: In the formula, N and N +1 represents the number of teeth on the inner and outer rotors, respectively. d The center distance between the inner and outer rotor profiles.

3. The conical modified in-line meshing twin-screw rotor structure according to claim 2, characterized in that, In coordinate system O 1 xy In the middle, the curved section of the inner rotor profile A 1 B 1 C 1 is obtained from the following calculation expression: In the formula, M i1 With M i2 Let each represent a rotation matrix, which is derived from the following equation: In the formula, ξ This represents the angle parameter variable, which is an intermediate parameter, and its relationship with the angle parameter is... θ The relationship between them is determined by the following formula: The range of values ​​for angular parameters α Determined by the following formula: 。 4. The conical modified in-line meshing twin-screw rotor structure according to claim 3, characterized in that, In coordinate system O 2 xy In the middle, the curved section of the outer rotor profile B 2 C The expression for calculating 2 is as follows: In the formula, M i1 With M i2 For the angle parameter variable ξ Expressions, parameter variables ξ and representing curve segments B 1 C Angular parameters of 1 θ The relationship between them conforms to the following expression: 。 5. The conical modified in-line meshing twin-screw rotor structure according to claim 1, characterized in that, The relationship between the outer diameter of the outer rotor profile and the center distance is as follows: In the formula, O 1 O e Center of the inner rotor profile O 1 and the center of the arc segment O e distance, d The center distance between the inner and outer rotor profiles.

6. The conical modified in-line meshing twin-screw rotor structure according to claim 1, characterized in that, The axial position of the outer rotor and the tooth tip radius of the corresponding profile conform to the following formula: In the formula, R 2( φ ( ) is the turning angle φ The tooth tip radius of the outer rotor profile at that time. The initial tooth tip radius of the outer rotor profile. L ( φ ( ) is the turning angle φ The corresponding rotor axial position and rotation angle φ This indicates the rotation angle of the rotor profile along the rotor's central axis. α The cone angle of the outer rotor; The rotor profiles at different axial positions have the same center distance, and the relationship between the rotor axial position and the rotor angle conforms to the following expression: In the formula, P ( φ () indicates rotor angle φ The corresponding pitch.

7. The conical modified in-line meshing twin-screw rotor structure according to claim 6, characterized in that, The radius of the generating circle of the outer rotor arc segment at different rotor axial positions is It satisfies the following relationship: In the formula, The radius of the generated circle of the outer rotor arc segment at the initial axial position of the rotor.

8. The conical modified in-line meshing twin-screw rotor structure according to claim 6, characterized in that, The distance between the center of the arc and the center of the outer rotor profile at different axial positions of the rotor is It satisfies the following relationship: In the formula, It is the distance between the center of the arc at the initial axial position of the rotor and the center of the inner rotor profile.

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