CN114151335A - Rotor end face tooth profile of high-temperature-resistant double-screw machine - Google Patents
Rotor end face tooth profile of high-temperature-resistant double-screw machine Download PDFInfo
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- CN114151335A CN114151335A CN202111409647.6A CN202111409647A CN114151335A CN 114151335 A CN114151335 A CN 114151335A CN 202111409647 A CN202111409647 A CN 202111409647A CN 114151335 A CN114151335 A CN 114151335A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
- F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
- F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/20—Rotors
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The tooth profile of the end face of the rotor of the high-temperature resistant double-screw machine is characterized in that the diameter of the outer circle of the female rotor is smaller than the diameter of the pitch circle of the female rotor, the tooth profile lines of the end face tooth profiles of the female rotor and the male rotor are formed by smoothly connecting seven sections of curves end to end, and the tooth profile of each tooth profile of the end face of the female rotor comprises a curve section A2B2, a circular arc section B2C2, a curve section C2D2, a curve section D2E2, a curve section E2F2, a circular arc section F2G2 and a circular arc section G2H2 which are sequentially connected. The tooth curve of each tooth type of the end face of the male rotor comprises a curve section A1B1, a curve section B1C1, a curve section C1D1, a circular arc section D1E1, a curve section E1F1, a curve section F1G1 and a circular arc section G1H 1. The small gap is reserved between the female rotor and the male rotor of the rotor end face tooth type, when the expansion allowance reaches a critical value at high temperature, the wiping position is small, the male rotor and the female rotor are not blocked, a section of small gap can be formed by grinding, and the tooth type is smooth without a cross point.
Description
Technical Field
The invention relates to a rotor end face tooth profile of a double-screw machine.
Background
The twin-screw machine comprises a twin-screw compressor, a twin-screw expander and the like, and rotors of the twin-screw machine run at different temperatures and have different thermal deformations, so that expansion allowance needs to be reserved in advance when rotor gaps are designed. In addition, the twin-screw machine has the advantages that the female rotor and the male rotor are meshed with each other to form the change of the volume between the teeth to realize compression or expansion, if the clearance of the rotors is designed to be smaller, when the temperature rises to a critical value with insufficient expansion allowance, the female rotor and the male rotor are rubbed and bumped, and when the temperature further rises, the rotors are possibly bitten and cannot continue to rotate. If the rotor clearance is designed to be larger and the gap between the rotors is too large, the leakage amount in the machine can be increased, and the working efficiency of the machine is reduced.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a rotor end face tooth profile of a double-screw machine, wherein a small gap is reserved between a female rotor and a male rotor of the rotor end face tooth profile, when the expansion allowance reaches a critical value at high temperature, the wiping position is small, the rotor end face tooth profile cannot be clamped, a section of small gap can be formed by running in, and the tooth profile is smooth without a cross point.
According to the rotor end face tooth profile of the high-temperature-resistant double-screw machine disclosed by the embodiment of the invention, the double-screw machine comprises a female rotor and a male rotor, and the excircle diameter of the female rotor is smaller than the pitch circle diameter of the female rotor; each tooth type of terminal surface of negative rotor and positive rotor's terminal surface is formed by seven sections curves smooth connection end to end, wherein: each tooth curve of the tooth type on the end surface of the female rotor comprises a curve section A2B2, an arc section B2C2, a curve section C2D2, a curve section D2E2, a curve section E2F2, an arc section F2G2 and an arc section G2H2 which are connected in sequence; the curved section A2B2, the curved section C2D2 and the curved section D2E2 of the female rotor are obtained by respectively converting an arc section A4B4, an elliptical arc section C4D4 and an arc enveloping line section D4E4 on a rack-shaped line from a rack-shaped line coordinate system to a female rotor coordinate system, and the curved section E2F2 of the female rotor is obtained by converting an arc section E3F3 on an engaging line of the female rotor and the male rotor from an engaging line coordinate system to a female rotor coordinate system; the tooth curves of the tooth types on the end surface of the male rotor comprise a curve section A1B1, a curve section B1C1, a curve section C1D1, a circular arc section D1E1, a curve section E1F1, a curve section F1G1 and a circular arc section G1H 1; the curve section A1B1, the curve section B1C1, the curve section C1D1 and the curve section F1G1 of the male rotor are obtained by converting an arc section A4B4, an arc enveloping section B4C4, an elliptical arc section C4D4 and an arc enveloping section F4G4 on a rack-shaped line from a rack-shaped line coordinate system to a male rotor coordinate system respectively, and the curve section E1F1 of the male rotor is obtained by converting an arc section E3F3 on an meshing line of the female rotor and the male rotor from a meshing line coordinate system to the male rotor coordinate system.
Compared with other tooth types, the rotor end face tooth type of the double-screw machine provided by the embodiment of the invention at least has the following advantages and characteristics:
1. the embodiment is different from the conventional single-side molded line (the excircle diameter of the female rotor is equal to the pitch circle diameter of the female rotor) and double-side molded line (the excircle diameter of the female rotor is greater than the pitch circle diameter of the female rotor), and the excircle diameter of the female rotor is smaller than the pitch circle diameter of the female rotor, so that the meshing of the rotors at the pitch circle position is avoided, and the self-running-in of the rotors is facilitated;
2. in the embodiment, the small arcs B2C2 and F2G2 are selected as the end face tooth-shaped component sections on the female rotor and the male rotor at positions which are easy to cause the rotor to swell and die due to rubbing, and the small arcs are in line contact when rubbing and touching occur, so that the range is small, the damage degree is small, certain self-grinding performance is realized, and the rotor is not easy to swell and die;
3. the curve section E2F2 of the female rotor and the curve section E1F1 of the male rotor are obtained by converting an arc section E3F3 on the meshing line of the female rotor and the male rotor from a meshing line coordinate system to a female rotor coordinate system and a male rotor coordinate system, so that the crossing point of tooth shapes can be eliminated, and the tooth shapes are smoother;
4. the tooth-shaped contact line of this embodiment length ratio is shorter, and it is very little to reveal the triangle-shaped, can neglect almost, has reduced the area that the rotor leaked, is favorable to improving the volumetric efficiency.
Drawings
Fig. 1 shows a tooth trace schematic of a female rotor according to an embodiment of the present invention.
Fig. 2 and 3 show partially enlarged schematic views of portions P1 and P2 of fig. 1, respectively.
FIG. 4 shows a tooth trace schematic of a male rotor according to an embodiment of the present invention.
Fig. 5 shows a partially enlarged schematic view of a portion P3 of fig. 4.
Fig. 6 shows a schematic view of rack profiles of a female rotor and a male rotor of an embodiment of the invention.
Fig. 7 shows a partially enlarged schematic view of a portion P4 of fig. 6.
FIG. 8 shows a schematic view of the meshing lines of the female and male rotors of an embodiment of the present invention.
Fig. 9 shows a partially enlarged schematic view of a portion P5 of fig. 8.
FIG. 10 shows a schematic view of a female rotor and a male rotor in mesh with each other according to an embodiment of the invention.
In the figure: om is the center Of the male rotor, and Of is the center Of the female rotor; l is the center distance between the female rotor and the male rotor.
Detailed Description
The rotor end face tooth type of the twin-screw compressor is described in detail with reference to the attached drawings and specific embodiments.
Please refer to fig. 1 to 10. A twin screw machine according to an embodiment of the invention comprises a female rotor F and a male rotor M. The number of teeth of the female rotor F is greater than that of the male rotor. The diameter of the outer circle of the female rotor F is smaller than the diameter of the pitch circle of the female rotor F. The end face of the female rotor F and the end face of the male rotor M are formed by connecting seven sections of curves end to end in a smooth manner.
Each tooth curve of the tooth type on the end surface of the female rotor comprises a curve section A2B2, an arc section B2C2, a curve section C2D2, a curve section D2E2, a curve section E2F2, an arc section F2G2 and an arc section G2H2 which are connected in sequence; the curved line segment A2B2, the curved line segment C2D2 and the curved line segment D2E2 of the female rotor are obtained by converting the arc segment A4B4, the elliptical arc segment C4D4 and the arc envelope line segment D4E4 on the rack-shaped line 400 from the rack-shaped line coordinate system to the female rotor coordinate system, and the curved line segment E2F2 of the female rotor is obtained by converting the arc segment E3F3 on the meshing line 300 of the female and male rotors from the meshing line coordinate system to the female rotor coordinate system, respectively.
The formula for converting the rack-type coordinate system into the female rotor coordinate system is as follows:
x2(t)＝x4(t)*cos(sitar2(t))+(y4(t)+R2t*sitar2)*sin(sitar2(t))；
y2(t)＝-x4(t)*sin(sitar2(t))+(y4(t)+R2t*sitar2)*cos(sitar2(t))；
sitar2(t)＝-(y4(t)-(R2t-x4(t))/k4(t))/R2t；
R2t＝A/(z1+z2)*z2；
wherein X4(t) and Y4(t) are X coordinates and Y coordinates of a rack-type line equation, k4(t) is a tangent slope of the rack-type line equation, sitar2(t) is an intermediate variable, R2t is a pitch circle radius of a female rotor, z1 is a tooth number of the male rotor, z2 is the tooth number of the female rotor, X2(t) and Y2(t) are X coordinates and Y coordinates of a female rotor end-face line equation, and t is a parameter.
The equation for converting the meshing line coordinate system into the female rotor coordinate system is as follows:
x2(t)＝x3(t)*cos(phi2(t))-y3(t)*sin(phi2(t))；
y2(t)＝x3(t)*sin(phi2(t))+y3(t)*cos(phi2(t))；
wherein X3(t) and Y3(t) are X coordinates and Y coordinates of a meshing line equation, k3(t) is a tangent slope of the meshing line equation, phi2(t) is an intermediate variable, R2t is a pitch circle radius of the female rotor, X2(t) and Y2(t) are X coordinates and Y coordinates of the female rotor end face profile equation, and t is a parameter.
In this embodiment, the arc segment B2C2 and the arc segment F2G2 are pre-designated self-grinding arcs of the rotor; the rotor self-grinding circular arcs are reserved with small gaps at positions, grinding can be carried out in the high-temperature thermal state operation process, the rotor self-grinding circular arcs are positions on the female rotor and the male rotor, the rotors are prone to swelling and death due to rubbing, in the embodiment, after the circular arc section B2C2 and the circular arc section F2G2 are selected as tooth-shaped component sections of the end face of the female rotor, due to the fact that line contact is achieved when rubbing occurs, the damage degree is small, certain self-grinding performance is achieved, and swelling and death are not prone to happening.
The tooth curves of the tooth types on the end surface of the male rotor comprise a curve section A1B1, a curve section B1C1, a curve section C1D1, a circular arc section D1E1, a curve section E1F1, a curve section F1G1 and a circular arc section G1H 1; the curve section A1B1, the curve section B1C1, the curve section C1D1 and the curve section F1G1 of the male rotor are obtained by converting an arc section A4B4, an arc enveloping section B4C4, an elliptical arc section C4D4 and an arc enveloping section F4G4 on a rack-shaped line from a rack-shaped line coordinate system to a male rotor coordinate system respectively, and the curve section E1F1 of the male rotor is obtained by converting an arc section E3F3 on an meshing line of the female rotor and the male rotor from a meshing line coordinate system to the male rotor coordinate system.
The formula for converting the rack profile coordinate system into the male rotor coordinate system is as follows:
x1(t)＝L-x4(t)*cos(sitar1(t))-(y4(t)+R1t*sitar1(t))*sin(sitar1(t))；
y1＝-x4(t)*sin(sitar1(t))+(y4(t)+R1t*sitar1(t))*cos(sitar1(t))；
sitar1(t)＝-(y4(t)-(R1t-x4(t))/k4(t))/R1t/z1*z2；
R2t＝L/(z1+z2)*z1；
wherein X4(t) and Y4(t) are X coordinates and Y coordinates of a rack profile equation, k4(t) is a tangent slope of the rack profile equation, sitar1(t) is an intermediate variable, R1t is a pitch circle radius of a male rotor, z1 is the number of teeth of the male rotor, z2 is the number of teeth of a female rotor, X1(t) and Y1(t) are the X coordinates and the Y coordinates of the end face profile equation of the male rotor, t is a parameter, and L is the center distance between the female rotor and the male rotor.
The equation for converting the meshing line coordinate system into the male rotor coordinate system is as follows:
x1(t)＝x3(t)*cos(phi1(t))-y3(t)*sin(phi1(t))；
y1(t)＝x3(t)*sin(phi1(t))+y3(t)*cos(phi1(t))；
wherein X3(t) and Y3(t) are X coordinates and Y coordinates of a meshing line equation, k3(t) is a tangent slope of the meshing line equation, phi1(t) is an intermediate variable, R1t is a pitch circle radius of the male rotor, and X1(t) and Y1(t) are X coordinates and Y coordinates of the end face profile equation of the male rotor.
The curved section E2F2 of the female rotor and the curved section E1F1 of the male rotor are obtained by respectively converting the arc section E3F3 on the meshing line of the female rotor and the male rotor from a meshing line coordinate system to a female rotor coordinate system and a male rotor coordinate system, so that the crossing point of the tooth forms can be eliminated, and the tooth forms are smoother.
In the present embodiment, in the rack profiles of the female rotor F and the male rotor M:
the circular arc section B2C2 of the female rotor is a circular arc with the radius of R2 and the center of O2 in the outer circle of the female rotor is as the center of a circle, R1 is n 2L, n2 is more than or equal to 0.03 and less than or equal to 0.1, and L is the center distance between the female rotor and the male rotor; the arc section F2G2 of the female rotor is an arc with the radius of R6 and the center of O6 in the excircle of the female rotor, wherein R6 is n 6L, and n2 is more than or equal to 0.03 and less than or equal to 0.1; the arc section G2H2 Of the female rotor is an arc with the radius Of R7f and the center Of Of as the center Of the circle, R7f is equal to half Of the outer diameter Of the female rotor, the radian b7f Of the arc section G2H2 is in the range Of 0 & lt b7f & lt 30 degrees, and the center Of the circle Of the female rotor is Of;
the arc section D1E1 of the male rotor is an arc with the radius of R4 and the center of O4 in the excircle of the male rotor, wherein R4 is n 4L, and n4 is more than or equal to 0.01 and less than or equal to 0.05; the arc section G1H1 of the male rotor is an arc with Om as the center and the radius of R7m, R7m is equal to half of the bottom diameter of the male rotor, and the radian b7m of the arc section G2H2 is as follows: b7m ═ b7f ═ z2/z1, z2 is the number of teeth of the female rotor, z1 is the number of teeth of the male rotor, and Om is the center of the circle of the male rotor.
Please refer to fig. 8 and 9. The meshing line of the end face tooth shapes of the female rotor and the male rotor is formed by smoothly connecting seven sections of curves end to end, and the seven sections of curves sequentially comprise a curve section A3B3, a curve section B3C3, a curve section C3D3, a curve section D3E3, an arc section E3F3, a curve section F3G3 and a curve section G3H 3; the starting point G3 and the end point H3 of the curve segment G3H3 and the starting point A3 of the curve segment A3B3 are the same point. In the embodiment, the arc segment E3F3 of the meshing line is an arc with a radius of R5 and with the center of O5 inside the outer circle of the female rotor, where R5 is n5 × L, and n5 is 0.01 ≦ n5 ≦ 0.1.
Please refer to fig. 6 and 7. In this embodiment, the rack profiles of the end face tooth profiles of the female rotor and the male rotor are formed by smoothly connecting seven sections of curves end to end, and the seven sections of curves sequentially include an arc section A4B4, an arc envelope line section B4C4, an elliptical arc section C4D4, an arc envelope line section D4E4, an envelope line section E4F4, an arc envelope line section F4G4 and a vertical line section G4H 4; wherein: an arc envelope line segment B4C4 is an envelope curve of an arc segment B2C2 of the female rotor on a rack-shaped line, an arc envelope line segment D4E4 is an envelope curve of an arc segment D1E1 of the male rotor on a rack-shaped line, an arc envelope line segment F4G4 is an envelope curve of an arc segment F2G2 of the female rotor on a rack-shaped line, an envelope curve segment E4F4 is an envelope curve segment E2F2 of the female rotor and an envelope curve segment E1F1 of the male rotor on a rack-shaped line (envelope curves of a curve segment E2F2 and a curve segment E1F1 on a rack-shaped line are the same envelope curve), a conjugate curve of a vertical line segment G4H4 on the female rotor is an arc segment G2H2, and a conjugate curve of a vertical line segment G4H4 on the male rotor is an arc segment G1H 1.
In the rack profile:
the arc section A4B4 is an arc with a radius of R1 and a circle center of O1, wherein R1 is n 1L, n1 is more than or equal to 0.01 and less than or equal to 0.05, and the circle center of O1 is on the same horizontal straight line with the starting point A4 of the arc section A4B 4;
the elliptical arc section C4D4 is an elliptical arc with the center of O3 outside the male rotor pitch circle, the major axis of R3a and the minor axis of R3 b; r3a ═ n3a × L, n3a < 0.3 ≤ 0.5; and R3B is n3B L, n3B is more than or equal to 0.1 and less than 0.3, an elliptical arc C4D4 is smoothly connected with an arc envelope line segment B4C4 at a starting point C4 and is smoothly connected with an arc envelope line segment D4E4 at an end point D4, the distance from a starting point C4 of the elliptical arc segment C4D4 to the center O3 is R3C, and the distance from an end point D4 of the elliptical arc segment C4D4 to the center O3 is R3D.
In a particular embodiment, the number of teeth z1 of the male rotor is 3, the number of teeth z2 of the female rotor is 6, and the rotor center-to-center distance L is equal to 160 mm. The outer diameters of the male rotor and the female rotor are both 204mm, the bottom diameters of the male rotor and the female rotor are both 116mm, the pitch circle diameter of the male rotor is 106.67mm, and the pitch circle diameter of the female rotor is 213.33 mm.
The rotor end face tooth profile of the double-screw compressor provided by the embodiment of the invention can be used for screw machines such as a screw compressor, a screw expander, a screw vacuum pump and a screw blower.
Claims (7)
1. The rotor end face tooth profile of the high-temperature resistant double-screw machine comprises a female rotor and a male rotor, and is characterized in that the excircle diameter of the female rotor is smaller than the pitch circle diameter of the female rotor; the end face of the female rotor and each tooth form of the end face of the male rotor are formed by connecting seven sections of curves end to end in a smooth mode, wherein:
each tooth curve of each tooth type on the end surface of the female rotor comprises a curve section A2B2, an arc section B2C2, a curve section C2D2, a curve section D2E2, a curve section E2F2, an arc section F2G2 and an arc section G2H2 which are connected in sequence; the curved section A2B2, the curved section C2D2 and the curved section D2E2 of the female rotor are obtained by respectively converting an arc section A4B4, an elliptical arc section C4D4 and an arc enveloping line section D4E4 on a rack-shaped line from a rack-shaped line coordinate system to a female rotor coordinate system, and the curved section E2F2 of the female rotor is obtained by converting an arc section E3F3 on an engaging line of the female rotor and the male rotor from an engaging line coordinate system to a female rotor coordinate system;
the tooth curves of the tooth types on the end surface of the male rotor comprise a curve section A1B1, a curve section B1C1, a curve section C1D1, a circular arc section D1E1, a curve section E1F1, a curve section F1G1 and a circular arc section G1H 1; the curve section A1B1, the curve section B1C1, the curve section C1D1 and the curve section F1G1 of the male rotor are obtained by converting an arc section A4B4, an arc enveloping section B4C4, an elliptical arc section C4D4 and an arc enveloping section F4G4 on a rack-shaped line from a rack-shaped line coordinate system to a male rotor coordinate system respectively, and the curve section E1F1 of the male rotor is obtained by converting an arc section E3F3 on an meshing line of the female rotor and the male rotor from a meshing line coordinate system to the male rotor coordinate system.
2. The rotor end face tooth profile of the double-screw machine as claimed in claim 1, wherein the circular arc section B2C2 of the female rotor is a circular arc with a radius of R2 and with a center of O2 inside the outer circle of the female rotor, R2 is n 2L, 0.03 is n2 is 0.1, and L is the center distance between the female rotor and the male rotor; the arc section F2G2 of the female rotor is an arc with the radius of R6 and the center of O6 in the excircle of the female rotor, wherein R6 is n 6L, and n2 is more than or equal to 0.03 and less than or equal to 0.1; the arc section G2H2 Of the female rotor is an arc with the radius Of R7f and the center Of Of as the center Of the circle, R7f is equal to half Of the outer diameter Of the female rotor, the radian b7f Of the arc section G2H2 is in the range Of 0 & lt b7f & lt 30 degrees, and the center Of the circle Of the female rotor is Of;
the arc section D1E1 of the male rotor is an arc with the radius of R4 and the center of O4 in the excircle of the male rotor, wherein R4 is n 4L, and n4 is more than or equal to 0.01 and less than or equal to 0.05; the arc section G1H1 of the male rotor is an arc with Om as the center and the radius of R7m, R7m is equal to half of the bottom diameter of the male rotor, and the radian b7m of the arc section G2H2 is as follows: b7m ═ b7f ═ z2/z1, z2 is the number of teeth of the female rotor, z1 is the number of teeth of the male rotor, and Om is the center of the circle of the male rotor.
3. The rotor end face tooth profile of the twin-screw machine according to claim 2, characterized in that the arc segment E3F3 of the meshing line is an arc with a radius R5 and with a center of O5 inside the outer circle of the female rotor, wherein R5 ═ n5 × L, and 0.01 ≦ n5 ≦ 0.1.
4. The rotor end face tooth profile of the double-screw machine as claimed in claim 1, wherein the rack profiles of the end face tooth profiles of the female rotor and the male rotor are formed by smoothly connecting seven sections of curves end to end, and the seven sections of curves sequentially comprise a circular arc section A4B4, a circular arc enveloping line section B4C4, an elliptical arc section C4D4, a circular arc enveloping line section D4E4, an enveloping curve section E4F4, a circular arc enveloping line section F4G4 and a vertical line section G4H 4; wherein: an arc envelope line segment B4C4 is an envelope curve of an arc segment B2C2 of the female rotor on a rack molded line, an arc envelope line segment D4E4 is an envelope curve of an arc segment D1E1 of the male rotor on the rack molded line, an arc envelope line segment F4G4 is an envelope curve of an arc segment F2G2 of the female rotor on the rack molded line, an envelope curve segment E4F4 is an envelope curve segment E2F2 of the female rotor and an envelope curve segment E1F1 of the male rotor on the rack molded line, a conjugate curve of a vertical line segment G4H4 on the female rotor is an arc segment G2H2, and a conjugate curve of a vertical line segment G4H4 on the male rotor is an arc segment G1H 1.
5. The rotor face profile of a twin screw machine as set forth in claim 4, wherein in the rack profile:
the arc section A4B4 is an arc with a radius of R1 and a circle center of O1, wherein R1 is n 1L, n1 is more than or equal to 0.01 and less than or equal to 0.05, and the circle center of O1 is on the same horizontal straight line with the starting point A4 of the arc section A4B 4;
the elliptical arc section C4D4 is an elliptical arc with the center of O3 outside the male rotor pitch circle, the major axis of R3a and the minor axis of R3 b; r3a ═ n3a × L, n3a < 0.3 ≤ 0.5; and R3B is n3B L, n3B is more than or equal to 0.1 and less than 0.3, and an elliptical arc C4D4 is smoothly connected with the circular arc envelope line segment B4C4 at the starting point C4 and is smoothly connected with the circular arc envelope line segment D4E4 at the terminal point D4.
6. Rotor end profile of a twin screw machine according to claim 1, characterized in that the number of teeth of the female rotor is greater than the number of teeth of the male rotor.
7. The rotor face profile of a twin screw machine according to claim 1, wherein the twin screw machine is a screw compressor, a screw expander, a screw vacuum pump or a screw blower.
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