CN114151335B - Rotor end face tooth type of high temperature resistant double screw machine - Google Patents
Rotor end face tooth type of high temperature resistant double screw machine Download PDFInfo
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- CN114151335B CN114151335B CN202111409647.6A CN202111409647A CN114151335B CN 114151335 B CN114151335 B CN 114151335B CN 202111409647 A CN202111409647 A CN 202111409647A CN 114151335 B CN114151335 B CN 114151335B
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Classifications
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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
-
- 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
-
- 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
Landscapes
- 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 formed by smoothly connecting seven sections of curves from beginning to end, wherein the tooth profile of the end face of the female rotor and the tooth profile of the end face of the male rotor comprise a curve section A2B2, a curve section B2C2, a curve section C2D2, a curve section D2E2, a curve section E2F2, a curve section F2G2 and a curve section G2H2 which are sequentially connected. The tooth curves of the teeth of the end face of the male rotor comprise curve sections A1B1, B1C1, C1D1, D1E1, E1F1, F1G1 and G1H1. The female rotor and the male rotor with the tooth-shaped rotor end surfaces are kept with smaller gaps, when the expansion allowance reaches a critical value at high temperature, the wiping and touching positions are smaller, the friction is not blocked, a section of smaller gap can be ground in, and the tooth shape is smoother without crossing points.
Description
Technical Field
The invention relates to a rotor end face tooth form of a double-screw machine.
Background
Twin screw machines include twin screw compressors, twin screw expanders, etc., where the rotors of the twin screw machines operate at different temperatures and there are different degrees of thermal deformation, and therefore expansion margins need to be reserved in designing rotor clearances. In addition, the twin-screw machine is characterized in that the female rotor and the male rotor are meshed with each other to form inter-tooth volume change to realize compression or expansion, if the rotor clearance is designed to be smaller, when the temperature rises to a critical value with insufficient expansion allowance, friction between the female rotor and the male rotor can occur, when the temperature further rises, the rotors possibly bite, and the rotation work cannot be continued. If the rotor clearance is designed to be larger, the gap between the rotors is too large, so that the leakage amount in the machine can be increased, and the working efficiency of the machine can be reduced.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a rotor end face tooth form of a double-screw machine, a small gap is reserved between a female rotor and a male rotor adopting the rotor end face tooth form, when the expansion allowance reaches a critical value at a high temperature, the wiping position is small, the friction position is not blocked, a section of small gap can be ground in, and the tooth form is smoother without crossing points.
According to the embodiment of the invention, the rotor end face tooth type double-screw machine comprises a female rotor and a male rotor, wherein the outer circle diameter of the female rotor is smaller than the pitch circle diameter of the female rotor; each tooth form of the terminal surface of female rotor and the terminal surface of male rotor is formed by seven sections of curve head and tail smooth connection, wherein: the tooth curves of each tooth type of the female rotor end face comprise 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 curve section A2B2, the curve section C2D2 and the curve section D2E2 of the female rotor are respectively obtained by converting a rack profile coordinate system into a female rotor coordinate system from a circular arc section A4B4, an elliptical arc section C4D4 and a circular arc envelope section D4E4 on a rack profile, and the curve section E2F2 of the female rotor is obtained by converting a circular arc section E3F3 on a meshing line of the female rotor and the male rotor from a meshing line coordinate system into a female rotor coordinate system; the tooth curves of each tooth type of the end face of the male rotor comprise curve sections A1B1, B1C1, C1D1, D1E1, E1F1, F1G1 and G1H1; the curve section A1B1, the curve section B1C1, the curve section C1D1 and the curve section F1G1 of the male rotor are respectively obtained by converting a rack profile coordinate system into a male rotor coordinate system from a circular arc section A4B4, a circular arc envelope section B4C4, an elliptical arc section C4D4 and a circular arc envelope section F4G4 on a rack profile, and the curve section E1F1 of the male rotor is obtained by converting a circular arc section E3F3 on a meshing line of the female rotor and the male rotor from a meshing line coordinate system into a male rotor coordinate system.
Compared with other tooth forms, the tooth form of the rotor end face of the double-screw machine provided by the embodiment of the invention has at least the following advantages and characteristics:
1. The embodiment is different from the conventional unilateral molded lines (the diameter of the outer circle of the female rotor is equal to the pitch diameter of the female rotor) and bilateral molded lines (the diameter of the outer circle of the female rotor is larger than the pitch diameter of the female rotor), and the diameter of the outer circle of the female rotor is smaller than the pitch diameter of the female rotor, so that the engagement of the rotor at the pitch position is avoided, and the self-running-in of the rotor is facilitated;
2. The small circular arcs B2C2 and F2G2 are selected as the component sections of the end face teeth on the female rotor and the male rotor, and the small circular arcs B2C2 and F2G2 are in line contact when rubbing, so that the range is small, the damage degree is small, the self-grinding performance is certain, and the female rotor is not easy to expand;
3. The curve section E2F2 of the female rotor and the curve section E1F1 of the male rotor are obtained by 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 intersection of tooth shapes can be eliminated, and the tooth shapes are smoother;
4. The length of the tooth-shaped contact line of the embodiment is shorter, the leakage triangle is very small and can be almost ignored, the leakage area of the rotor is reduced, and the volumetric efficiency is improved.
Drawings
Fig. 1 shows a schematic diagram of a tooth profile of a female rotor according to an embodiment of the present invention.
Fig. 2 and 3 show partial enlarged schematic views of the P1 portion and the P2 portion of fig. 1, respectively.
Fig. 4 shows a schematic diagram of tooth profile of a male rotor according to an embodiment of the present invention.
Fig. 5 shows a partially enlarged schematic view of the portion P3 of fig. 4.
Fig. 6 shows a schematic view of a rack profile of a female rotor and a male rotor according to an embodiment of the present invention.
Fig. 7 shows a partially enlarged schematic view of the portion P4 of fig. 6.
Fig. 8 shows a schematic view of the meshing lines of the female rotor and the male rotor of an embodiment of the present invention.
Fig. 9 shows a partially enlarged schematic view of the portion P5 of fig. 8.
Fig. 10 shows a schematic view of a female rotor and a male rotor of an embodiment of the present invention when intermeshed.
In the figure: om is the center Of the male rotor, and Of is the center Of the female rotor; l is the center-to-center distance of the female rotor and the male rotor.
Detailed Description
The present invention is described in detail below with reference to the drawings and specific examples of the present invention.
Please refer to fig. 1 to 10. The twin screw machine according to an embodiment of the present invention includes 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 outer diameter of the female rotor F is smaller than the pitch diameter 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 smoothly connecting seven sections of curves end to end.
The tooth curves of each tooth type of the female rotor end face comprise 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 curve segments A2B2, C2D2 and D2E2 of the female rotor are respectively obtained by converting the rack profile coordinate system to the female rotor coordinate system from the arc segments A4B4, C4D4 and D4E4 on the rack profile 400, and the curve 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.
The formula for converting the rack profile coordinate system into the female rotor coordinate system is shown 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 the X coordinate and the Y coordinate of the rack profile equation, k4 (t) is the tangential slope of the rack profile equation, sitar (t) is an intermediate variable, R2t is the radius of the pitch circle of the female rotor, z1 is the number of teeth of the male rotor, z2 is the number of teeth of the female rotor, X2 (t) and Y2 (t) are the X coordinate and the Y coordinate of the end surface profile equation of the female rotor, and t is a parameter.
The equation for transforming the meshing line coordinate system into the female rotor coordinate system is shown below:
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 the X coordinate and the Y coordinate of the meshing line equation, k3 (t) is the tangential slope of the meshing line equation, phi2 (t) is an intermediate variable, R2t is the radius of the pitch circle of the female rotor, X2 (t) and Y2 (t) are the X coordinate and the Y coordinate of the end face line equation of the female rotor, and t is a parameter.
In this embodiment, the arc segments B2C2 and F2G2 are self-grinding arcs of the rotor specified in advance; the rotor self-grinding circular arc is provided with a small gap in advance, grinding can be carried out in the high-temperature hot state operation process, and the rotor self-grinding circular arc is a position on the female rotor and the male rotor, which is easy to expand and die because of friction, and the rotor self-grinding circular arc is small in damage degree and difficult to expand and die because the female rotor is in line contact when friction occurs after the circular arc section B2C2 and the circular arc section F2G2 are selected as the component sections of the end face teeth of the female rotor.
The tooth curves of each tooth type of the end face of the male rotor comprise curve sections A1B1, B1C1, C1D1, D1E1, E1F1, F1G1 and G1H1; the curve section A1B1, the curve section B1C1, the curve section C1D1 and the curve section F1G1 of the male rotor are respectively obtained by converting a rack profile coordinate system into a male rotor coordinate system from a circular arc section A4B4, a circular arc envelope section B4C4, an elliptical arc section C4D4 and a circular arc envelope section F4G4 on a rack profile, and the curve section E1F1 of the male rotor is obtained by converting a circular arc section E3F3 on a meshing line of the female rotor and the male rotor from a meshing line coordinate system into a male rotor coordinate system.
The formula for converting the rack profile coordinate system into the male rotor coordinate system is shown 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 the X coordinate and the Y coordinate of the rack profile equation, k4 (t) is the tangential slope of the rack profile equation, sitar (t) is an intermediate variable, R1t is the pitch circle radius of the male rotor, z1 is the number of teeth of the male rotor, z2 is the number of teeth of the female rotor, X1 (t) and Y1 (t) are the X coordinate and the Y coordinate 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 transforming the meshing line coordinate system into the male rotor coordinate system is shown below:
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 the X coordinate and the Y coordinate of the meshing line equation, k3 (t) is the tangential slope of the meshing line equation, phi1 (t) is an intermediate variable, R1t is the pitch circle radius of the male rotor, and X1 (t) and Y1 (t) are the X coordinate and the Y coordinate of the end face line equation of the male rotor.
The curve segment E2F2 of the female rotor and the curve segment E1F1 of the male rotor are respectively obtained by converting the arc segment 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 intersection of tooth patterns can be eliminated, and the tooth patterns are smoother.
In this embodiment, in the rack profile of the female rotor F and the male rotor M:
the arc section B2C2 of the female rotor is an arc section with the O2 inside the outer circle of the female rotor as the center of a circle and the radius of R2, R1=n2 is equal to or less than 0.03 and equal to or less than 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 by taking O6 inside the outer circle of the female rotor as the center, R6 = n6 x L, 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 Of as a circle center and the radius Of R7f, R7f is equal to half Of the outer diameter Of the female rotor, the value range Of the radian b7f Of the arc section G2H2 is more than 0 and less than 30 degrees, and the Of is the circle center Of the female rotor;
The arc section D1E1 of the male rotor is an arc section with the radius R4 by taking O4 inside the outer circle of the male rotor as the center, R4 = n4 x L, 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 a section of arc taking Om as a circle center and having a radius R7m, R7m is equal to half of the bottom radius of the male rotor, and the radian b7m of the arc section G2H2 is as follows: b7m=b7f.z2/z 1, 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 male rotor.
Please refer to fig. 8 and 9. The meshing line of the end face teeth of the female rotor and the male rotor is formed by smoothly connecting seven sections of curves from beginning to end, wherein the seven sections of curves sequentially comprise a curve section A3B3, a curve section B3C3, a curve section C3D3, a curve section D3E3, a circular arc section E3F3, a curve section F3G3 and a curve section G3H3; the starting point G3, the ending point H3 of the curve segment G3H3, and the starting point A3 of the curve segment A3B3 are the same point. In this embodiment, the arc segment E3F3 of the meshing line is an arc segment with a radius R5 and a center of O5 inside the outer circle of the female rotor, where r5=n5×l, and 0.01 n5 is less than or equal to 0.1.
Please refer to fig. 6 and 7. In this embodiment, the rack profile of the end face teeth of the female rotor and the male rotor is formed by smoothly connecting the ends of seven curves, and the seven curves sequentially include an arc section A4B4, an arc envelope section B4C4, an elliptical arc section C4D4, an arc envelope section D4E4, an envelope curve section E4F4, an arc envelope section F4G4 and a vertical section G4H4; wherein: the circular arc envelope line segment B4C4 is an envelope of a circular arc segment B2C2 of the female rotor on the rack type line, the circular arc envelope line segment D4E4 is an envelope of a circular arc segment D1E1 of the male rotor on the rack type line, the circular arc envelope line segment F4G4 is an envelope of a circular arc segment F2G2 of the female rotor on the rack type line, the envelope curve line segment E4F4 is an envelope of a curve segment E2F2 of the female rotor and an envelope of a curve segment E1F1 of the male rotor on the rack type line (the envelopes of the curve segment E2F2 and the curve segment E1F1 on the rack type line are the same envelope line), a conjugate curve of the vertical line segment G4H4 on the female rotor is a circular arc segment G2H2, and a conjugate curve of the vertical line segment G4H4 on the male rotor is a circular arc segment G1H1.
Rack molded lines:
The arc section A4B4 is a section of arc with O1 as the center and the radius of R1, R1=n1 is L, n1 is more than or equal to 0.01 and less than or equal to 0.05, and the center O1 and the starting point A4 of the arc section A4B4 are on the same horizontal straight line;
The elliptical arc section C4D4 is an elliptical arc section which takes O3 outside the pitch circle of the male rotor as a center, takes the major axis as R3a and takes the minor axis as R3 b; r3a=n 3a is a number L of times the number of the active ingredients, n3a is more than 0.3 and less than or equal to 0.5; r3b=n3b×l, 0.1+.n3b < 0.3, elliptic arc C4D4 is smoothly connected with circular arc envelope segment B4C4 at start point C4, is smoothly connected with circular arc envelope segment D4E4 at end point D4, the distance from start point C4 to center O3 of elliptic arc segment C4D4 is R3C, and the distance from end point D4 to center O3 of elliptic arc segment C4D4 is R3D.
In a specific 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 distance L is 160mm. The outer diameters of the male rotor and the female rotor are 204mm, the bottom diameters of the male rotor and the female rotor are 116mm, the pitch circle diameter of the male rotor is 106.67mm, and the pitch circle diameter of the female rotor is 213.33mm.
The rotor end face tooth type double-screw compressor can be used for screw machines such as screw compressors, screw expanders, screw vacuum pumps, screw blowers and the like.
Claims (6)
1. The rotor end face tooth type double-screw machine resistant to high temperature comprises a female rotor and a male rotor, and is characterized in that the diameter of the outer circle of the female rotor is smaller than the pitch diameter of the female rotor; each tooth form of the end face of the female rotor and the end face of the male rotor is formed by smoothly connecting seven sections of curves end to end, wherein:
The tooth curves of each tooth type of the female rotor end face comprise 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 curve section A2B2, the curve section C2D2 and the curve section D2E2 of the female rotor are respectively obtained by converting a rack profile coordinate system into a female rotor coordinate system from a circular arc section A4B4, an elliptical arc section C4D4 and a circular arc envelope section D4E4 on a rack profile, and the curve section E2F2 of the female rotor is obtained by converting a circular arc section E3F3 on a meshing line of the female rotor and the male rotor from a meshing line coordinate system into a female rotor coordinate system;
The tooth curves of each tooth type of the end face of the male rotor comprise curve sections A1B1, B1C1, C1D1, D1E1, E1F1, F1G1 and G1H1; the curve section A1B1, the curve section B1C1, the curve section C1D1 and the curve section F1G1 of the male rotor are respectively obtained by converting a rack molded line coordinate system into a male rotor coordinate system from a rack molded line, namely a circular arc section A4B4, a circular arc envelope section B4C4, an elliptical arc section C4D4 and a circular arc envelope section F4G4 on a rack molded line, and the curve section E1F1 of the male rotor is obtained by converting a circular arc section E3F3 on a meshing line of the female rotor and the male rotor from a meshing line coordinate system into a male rotor coordinate system;
The arc section B2C2 of the female rotor is an arc section with the O2 inside the outer circle of the female rotor as the center of a circle and the radius of R2, R2 = n2 is equal to or less than 0.03 and equal to or less than 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 by taking O6 inside the outer circle of the female rotor as the center, R6 = n6 x L, 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 Of as a circle center and the radius Of R7f, R7f is equal to half Of the outer diameter Of the female rotor, the value range Of the radian b7f Of the arc section G2H2 is more than 0 and less than 30 degrees, and the Of is the circle center Of the female rotor;
The arc section D1E1 of the male rotor is an arc section with the radius R4 by taking O4 inside the outer circle of the male rotor as the center, R4 = n4 x L, 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 a section of arc taking Om as a circle center and having a radius R7m, R7m is equal to half of the bottom radius of the male rotor, and the radian b7m of the arc section G2H2 is as follows: b7m=b7f.z2/z 1, 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 male rotor.
2. The rotor end face tooth form of claim 1, wherein the arc segment E3F3 of the meshing line is an arc with a radius R5 around O5 inside the outer circle of the female rotor, r5=n5×l, and 0.01.ltoreq.n5.ltoreq.0.1.
3. The rotor end face tooth form of the twin-screw machine according to claim 1, wherein the rack profile of the end face tooth form of the female rotor and the male rotor is formed by smoothly connecting seven sections of curves from end to end, and the seven sections of curves sequentially comprise an arc section A4B4, an arc envelope section B4C4, an elliptical arc section C4D4, an arc envelope section D4E4, an envelope curve section E4F4, an arc envelope section F4G4 and a vertical section G4H4; wherein: the circular arc envelope line segment B4C4 is the envelope line of the circular arc segment B2C2 of the female rotor on the rack type line, the circular arc envelope line segment D4E4 is the envelope line of the circular arc segment D1E1 of the male rotor on the rack type line, the circular arc envelope line segment F4G4 is the envelope line of the circular arc segment F2G2 of the female rotor on the rack type line, the envelope curve line segment E4F4 is the envelope line of the curve segment E2F2 of the female rotor and the envelope line of the curve segment E1F1 of the male rotor on the rack type line, the conjugate line of the vertical line segment G4H4 on the female rotor is the circular arc segment G2H2, and the conjugate line of the vertical line segment G4H4 on the male rotor is the circular arc segment G1H1.
4. A rotor end face tooth form for a twin screw machine as defined in claim 3, wherein in said rack profile:
The arc section A4B4 is a section of arc with O1 as the center and the radius of R1, R1=n1 is L, n1 is more than or equal to 0.01 and less than or equal to 0.05, and the center O1 and the starting point A4 of the arc section A4B4 are on the same horizontal straight line;
The elliptical arc section C4D4 is an elliptical arc section which takes O3 outside the pitch circle of the male rotor as a center, takes the major axis as R3a and takes the minor axis as R3 b; r3a=n 3a is a number L of times the number of the active ingredients, n3a is more than 0.3 and less than or equal to 0.5; r3b=n3b×l, 0.1+.n3b < 0.3, the elliptical arc C4D4 is smoothly connected with the circular arc envelope segment B4C4 at the start point C4 and with the circular arc envelope segment D4E4 at the end point D4.
5. The rotor end face tooth form of claim 1, wherein said female rotor has a number of teeth greater than a number of teeth of said male rotor.
6. The rotor end face tooth form of a twin screw machine as defined in 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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| CN102900672B (en) * | 2011-07-27 | 2017-02-08 | 中国船舶重工集团公司第七一一研究所 | Rotor of oil-free screw compressor |
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| CN109026163B (en) * | 2018-09-18 | 2023-08-08 | 上海齐耀膨胀机有限公司 | Tooth type of rotor of high-pressure ratio high-pressure difference double-screw expander |
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