CN114033680A - Rotor end face tooth form of double-screw machine with self-running-in capacity - Google Patents
Rotor end face tooth form of double-screw machine with self-running-in capacity Download PDFInfo
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- CN114033680A CN114033680A CN202111279171.9A CN202111279171A CN114033680A CN 114033680 A CN114033680 A CN 114033680A CN 202111279171 A CN202111279171 A CN 202111279171A CN 114033680 A CN114033680 A CN 114033680A
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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
- 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
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
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- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The rotor end face tooth profile of the double-screw machine with self-grinding capability, the excircle diameter of the female rotor is smaller than the pitch circle diameter; the rack molded lines of the end face tooth shapes of the female rotor and the male rotor are formed by smoothly connecting nine sections of curves end to end, and the nine sections of curves sequentially comprise an arc section AB, a point envelope curve section BC, an inclined straight section CD, an elliptical arc section DE, a point envelope curve section EF, a trochoid section FG, a point envelope curve section GH, an arc section HI and a vertical line section IJ; the end face of the female rotor and the end face of the male rotor are respectively formed by connecting nine sections of curves end to end in a smooth mode, and the nine sections of curves of the rack molded lines can be obtained through coordinate conversion respectively. 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, and a small gap can be formed by grinding.
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 which adopt the rotor end face tooth profile, and when the expansion allowance reaches a critical value at high temperature, the wiping position is small, the rotor end face tooth profile cannot be blocked, and a small gap can be formed by running in.
According to the rotor end face tooth profile of the double-screw machine with the self-running-in capacity, the double-screw machine comprises a female rotor and a male rotor, wherein the excircle diameter of the female rotor is smaller than the pitch circle diameter of the female rotor; the rack molded lines of the end face tooth shapes of the female rotor and the male rotor are formed by smoothly connecting nine sections of curves end to end, and the nine sections of curves sequentially comprise an arc section AB, a point envelope curve section BC, an inclined straight section CD, an elliptical arc section DE, a point envelope curve section EF, a trochoid section FG, a point envelope curve section GH, an arc section HI and a vertical line section IJ; each tooth type of terminal surface of negative rotor and positive rotor's terminal surface is formed by nine sections curves smooth connections end to end, wherein: the tooth curve of each tooth type on the end face of the female rotor comprises a curve section A2B2, a curve section B2C2, a curve section C2D2, a curve section D2E2, a curve section E2F2, a curve section F2G2, a curve section G2H2, a curve section H2I2 and a curve section I2J2 which are connected in sequence, and the tooth curve of each tooth type on the end face of the male rotor comprises a curve section A1B1, a curve section B1C1, a curve section C1D1, a curve section D1E1, a curve section E1F1, a curve section F1G1, a curve section G1H1, a curve section H1I1 and a curve section I1J 1; wherein, the starting point B2 and the end point C2 of the curve segment B2C2 are the same point, the starting point G2 and the end point H2 of the curve segment G2H2 are the same point, and the starting point E1 and the end point F1 of the curve segment E1F1 are the same point; the starting point B2 and the end point C2, the starting point G2 and the end point H2, and the starting point E1 and the end point F1 are all self-running-in points of the rotor which are designated in advance;
curve segment A2B2, curve segment B2C2, curve segment C2D2, curve segment D2E2, curve segment E2F2, curve segment F2G2, curve segment G2H2, curve segment H2I2 and curve segment I2J2 are obtained by respectively converting arc segment AB, point envelope curve segment BC, oblique straight line segment CD, elliptical arc segment DE, point envelope curve segment EF, trochoid segment FG, point envelope curve segment GH, arc segment HI and vertical line segment IJ from a rack-type line coordinate system to a female rotor coordinate system, and curve segment A1B1, curve segment B1C1, curve segment C1D1, curve segment D1E1, curve segment E1F1, curve segment F1G1, curve segment G1H1, curve segment H1I1 and curve segment I1J1 are obtained by respectively converting arc segment AB, point envelope curve segment CD, oblique envelope curve segment BC, point envelope curve segment hf 1G, point envelope curve segment GH, rack-type line segment GH and vertical line coordinate system from a rack-type line coordinate system to a female 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 (referred to as a half-side molded line in the application), 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, points and envelope lines (cycloid) thereof are selected as tooth-shaped component sections of the end faces of the female rotor and the male rotor (point B2, point C2, point G2 and point H2 of the tooth shape of the female rotor, point E1 and point F1 of the tooth shape of the male rotor) at positions on the female rotor and the male rotor which are easy to cause rotor swelling due to rubbing, and the points are in line contact when rubbing occurs, so that the damage degree is small, certain self-grinding performance is realized, and swelling is not easy to occur;
3. 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
Figure 1 shows a tooth trace schematic of one embodiment of the female rotor of the present invention.
Figure 2 shows a tooth trace schematic of one embodiment of the male rotor of the present invention.
Fig. 3 shows a schematic view of rack profiles of a female rotor and a male rotor of an embodiment of the invention.
Figure 4 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 4. A twin screw machine according to an embodiment of the invention comprises a female rotor F and a male rotor M. 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 pitch circle diameter of the female rotor F is larger than that of the male rotor M, and the number of teeth of the female rotor F is larger than that of the male rotor (the ratio of the numbers of teeth of the female rotor and the male rotor is equal to the ratio of the pitch circle diameters). In order to obtain better working performance, the number of teeth of the female rotor F is optionally more than 2 (including 2 more teeth) more than the number of teeth of the male rotor M.
Each tooth type of the end surface of the female rotor F and the end surface of the male rotor M is formed by connecting nine sections of curves end to end in a smooth mode, wherein: the tooth curve of each tooth type on the end face of the female rotor comprises a curve section A2B2, a curve section B2C2, a curve section C2D2, a curve section D2E2, a curve section E2F2, a curve section F2G2, a curve section G2H2, a curve section H2I2 and a curve section I2J2 which are connected in sequence, and the tooth curve of each tooth type on the end face of the male rotor comprises a curve section A1B1, a curve section B1C1, a curve section C1D1, a curve section D1E1, a curve section E1F1, a curve section F1G1, a curve section G1H1, a curve section H1I1 and a curve section I1J 1; wherein, the starting point B2 and the end point C2 of the curve segment B2C2 are the same point, the starting point G2 and the end point H2 of the curve segment G2H2 are the same point, and the starting point E1 and the end point F1 of the curve segment E1F1 are the same point; the starting point B2 and the end point C2, the starting point G2 and the end point H2, and the starting point E1 and the end point F1 are all pre-designated rotor self-running-in points; the rotor self-grinding points are reserved with small gaps at positions, the rotors can be ground in the high-temperature thermal state operation process, the rotor self-grinding points are positions on the female rotor and the male rotor, the rotors are prone to swelling and death due to rubbing, and after the points and the envelope lines (cycloid) of the points are selected as the tooth-shaped component sections of the end faces of the female rotor and the male rotor, due to the fact that line contact is achieved when rubbing occurs, the rotor self-grinding points are small in damage degree and have certain self-grinding performance, and swelling and death are not prone to happening.
The rack molded lines of the end face tooth shapes of the female rotor F and the male rotor M are formed by smoothly connecting nine sections of curves end to end, and the nine sections of curves sequentially comprise an arc section AB, a point envelope curve section BC, an inclined straight section CD, an elliptical arc section DE, a point envelope curve section EF, a trochoid section FG, a point envelope curve section GH, an arc section HI and a vertical line section IJ.
In the present embodiment, in the rack profiles of the female rotor F and the male rotor M:
the arc section AB is a section of arc with the radius of R1 and the center of O1, R1 is n 1L, n1 is more than or equal to 0.01 and less than or equal to 0.05, L is the center distance between the female rotor and the male rotor, and the center of O1 and the starting point A of the arc section AB are on the same horizontal straight line;
a point envelope curve segment BC is an envelope curve of a point B2 or a point C2 on a tooth curve of the end face of the female rotor on the molded line of the rack, namely a segment of cycloid;
the inclined straight line segment CD is an inclined straight line connecting the point C and the point D;
the elliptical arc section DE is an elliptical arc with the center of O2, the major axis of R2a and the minor axis of R2 b; r2a ═ n2 × L, 0.3 ≤ n2 ≤ 0.5; r2b is n 3L, and n3 is not less than 0.1 and not more than 0.3; the tangent line of the starting point D of the elliptical arc section DE and the inclined straight line section CD are on the same straight line, and the tangent direction of the end point E of the elliptical arc section DE is in the vertical direction; the distance from the point D to the center O2 of the elliptical arc section DE is R2D, and the distance from the point E to the center O2 of the elliptical arc section DE is R2E;
the point envelope curve segment EF is an envelope curve of an E1 point or an F1 point on a male rotor face tooth curve on a rack profile, namely a segment of cycloid;
the trochoid section FG is an envelope curve of an arc F2G2 on a pre-designated female rotor end face tooth curve on a rack profile, the circle center of the arc F2G2 on the pre-designated female rotor end face tooth curve is O4, the radius is R4, the circle center O4 is positioned inside a female rotor pitch circle, R4 is n4 x L, n4 is more than or equal to 0.3 and less than or equal to 0.8, and the trochoid section FG is tangent to a point envelope curve section EF at a point F;
the point envelope curve segment GH is an envelope curve of a G2 point or an H2 point on a female rotor face tooth curve on a rack profile, namely a segment of cycloid;
the arc section HI is an arc with the radius of R3 and the center of O3, R3 is n 5L, n5 is more than or equal to 0.03 and less than or equal to 0.1, and the center of O3 and the end point I of the arc section HI are on the same horizontal straight line;
the vertical straight line segment IJ is a vertical straight line.
The curve segment A2B2, the curve segment B2C2, the curve segment C2D2, the curve segment D2E2, the curve segment E2F2, the curve segment F2G2, the curve segment G2H2, the curve segment H2I2 and the curve segment I2J2 are respectively obtained by converting an arc segment AB, a point envelope curve segment BC, an inclined straight segment CD, an elliptical arc segment DE, a point envelope curve segment EF, a trochoid segment FG, a point envelope curve segment GH, an arc segment HI and a vertical line segment IJ from a rack-line coordinate system to a female rotor coordinate system, and the formula for converting the rack-line coordinate system to the female rotor coordinate system is as follows:
xs2(t)＝xr(t).*cos(sitar2(t))+[yr(t)+R2t*sitar2(t)].*sin(sitar2(t))；
ys2(t)＝-xr(t).*sin(sitar2(t))+[yr(t)+R2t*sitar2(t)].*cos(sitar2(t))；
sitar2(t)＝-{yr(t)-[R2t-xr(t)]/kr(t)}/R2t；
R2t＝L/(z1+z2)*z2；
wherein xr (t), yr (t) are the X coordinate and the Y coordinate of the rack-type line equation, kr (t) is the slope of the tangent line of the rack-type line equation, sitar2(t) is an intermediate variable, R2t is the radius of the female rotor pitch circle, z1 is the number of male rotor teeth, z2 is the number of female rotor teeth, xs2(t), ys2(t) are the X coordinate and the Y coordinate of the female rotor end-face line equation, and t is a parameter.
The curve segment A1B1, the curve segment B1C1, the curve segment C1D1, the curve segment D1E1, the curve segment E1F1, the curve segment F1G1, the curve segment G1H1, the curve segment H1I1 and the curve segment I1J1 are respectively obtained by converting an arc segment AB, a point envelope curve segment BC, an inclined straight segment CD, an elliptical arc segment DE, a point envelope curve segment EF, a trochoid segment FG, a point envelope curve segment GH, an arc segment HI and a vertical line segment IJ from a rack-line coordinate system to a male rotor coordinate system, and the formula for converting the rack-line coordinate system to the male rotor coordinate system is as follows:
xs1(t)＝L-xr(t).*cos(sitar1(t))-[yr(t)+R1t*sitar1(t)].*sin(sitar1(t))；
ys1(t)＝-xr(t).*sin(sitar1(t))+[yr(t)+R1t*sitar1(t)].*cos(sitar1(t))；
sitar1(t)＝-{yr(t)-[R1t-xr(t)]/kr(t)}/R1t/z1*z2；
R1t＝L/(z1+z2)*z1；
wherein xr (t), yr (t) are the X coordinate and the Y coordinate of the rack-type line equation, kr (t) is the slope of the tangent line of the rack-type line equation, sitar1(t) is an intermediate variable, R1t is the radius of the male rotor pitch circle, z1 is the male rotor tooth number, z2 is the female rotor tooth number, xs1(t), ys1(t) are the X coordinate and the Y coordinate of the male rotor end-face line equation, and t is a parameter. In one specific embodiment, as shown in fig. 4, the number of teeth of the male rotor is 3, the number of teeth 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 (5)
1. The rotor end face tooth profile of a double-screw machine with self-running-in capability, wherein the 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 rack molded lines of the end face tooth shapes of the female rotor and the male rotor are formed by smoothly connecting nine sections of curves end to end, and the nine sections of curves sequentially comprise an arc section AB, a point envelope curve section BC, an inclined straight section CD, an elliptical arc section DE, a point envelope curve section EF, a trochoid section FG, a point envelope curve section GH, an arc section HI and a vertical line section IJ;
the end face of the female rotor and each tooth form of the end face of the male rotor are formed by connecting nine sections of curves end to end in a smooth mode, wherein: the tooth curve of each tooth type of the female rotor end face comprises a curve section A2B2, a curve section B2C2, a curve section C2D2, a curve section D2E2, a curve section E2F2, a curve section F2G2, a curve section G2H2, a curve section H2I2 and a curve section I2J2 which are connected in sequence, and the tooth curve of each tooth type of the male rotor end face comprises a curve section A1B1, a curve section B1C1, a curve section C1D1, a curve section D1E1, a curve section E1F1, a curve section F1G1, a curve section G1H1, a curve section H1I1 and a curve section I1J 1; wherein, the starting point B2 and the end point C2 of the curve segment B2C2 are the same point, the starting point G2 and the end point H2 of the curve segment G2H2 are the same point, and the starting point E1 and the end point F1 of the curve segment E1F1 are the same point; the starting point B2 and the end point C2, the starting point G2 and the end point H2, and the starting point E1 and the end point F1 are all self-running-in points of the rotor which are designated in advance;
curve segment A2B2, curve segment B2C2, curve segment C2D2, curve segment D2E2, curve segment E2F2, curve segment F2G2, curve segment G2H2, curve segment H2I2 and curve segment I2J2 are obtained by respectively converting arc segment AB, point envelope curve segment BC, oblique straight line segment CD, elliptical arc segment DE, point envelope curve segment EF, trochoid segment FG, point envelope curve segment GH, arc segment HI and vertical line segment IJ from a rack-type line coordinate system to a female rotor coordinate system, and curve segment A1B1, curve segment B1C1, curve segment C1D1, curve segment D1E1, curve segment E1F1, curve segment F1G1, curve segment G1H1, curve segment H1I1 and curve segment I1J1 are obtained by respectively converting arc segment AB, point envelope curve segment CD, oblique envelope curve segment BC, point envelope curve segment hf 1G, point envelope curve segment GH, rack-type line segment GH and vertical line coordinate system from a rack-type line coordinate system to a female rotor coordinate system.
2. The rotor face profile of a twin screw machine as set forth in claim 1, wherein in the rack profile: the arc section AB is a section of arc with the radius of R1 and the center of O1, R1 is n 1L, n1 is more than or equal to 0.01 and less than or equal to 0.05, L is the center distance between the female rotor and the male rotor, and the center of O1 and the starting point A of the arc section AB are on the same horizontal straight line;
a point envelope curve segment BC is an envelope curve of a point B2 or a point C2 on a tooth curve of a female rotor end face on a rack profile;
the inclined straight line segment CD is an inclined straight line connecting the point C and the point D;
the elliptical arc section DE is an elliptical arc with the center of O2, the major axis of R2a and the minor axis of R2 b; r2a ═ n2 × L, 0.3 ≤ n2 ≤ 0.5; r2b is n 3L, n3 is 0.1 or more and is 0.3 or less, the tangent of the starting point D of the elliptical arc segment DE and the inclined straight line segment CD are on the same straight line, and the tangent direction of the end point E of the elliptical arc segment DE is in the vertical direction;
the point envelope curve segment EF is an envelope curve of an E1 point or an F1 point on a male rotor face tooth curve on a rack profile;
the trochoid section FG is an envelope curve of an arc F2G2 on a pre-designated female rotor end face tooth curve on a rack profile, the circle center of the arc F2G2 on the pre-designated female rotor end face tooth curve is O4, the radius is R4, the circle center O4 is positioned inside a female rotor pitch circle, R4 is n4 x L, n4 is more than or equal to 0.3 and less than or equal to 0.8, and the trochoid section FG is tangent to a point envelope curve section EF at a point F;
the point envelope curve segment GH is an envelope curve of a G2 point or an H2 point on a female rotor face tooth curve on a rack profile;
the arc section HI is an arc with the radius of R3 and the center of O3, R3 is n 5L, n5 is more than or equal to 0.03 and less than or equal to 0.1, and the center of O3 and the end point I of the arc section HI are on the same horizontal straight line;
the vertical straight line segment IJ is a vertical straight line.
3. 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.
4. The rotor face profile of a twin screw machine as set forth in claim 1, wherein the number of teeth of the female rotor is more than 2 than the number of teeth of the male rotor.
5. 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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| CN202111279171.9A CN114033680A (en) | 2021-10-31 | 2021-10-31 | Rotor end face tooth form of double-screw machine with self-running-in capacity |
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| CN202111279171.9A CN114033680A (en) | 2021-10-31 | 2021-10-31 | Rotor end face tooth form of double-screw machine with self-running-in capacity |
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| CN109026163A (en) * | 2018-09-18 | 2018-12-18 | 上海齐耀膨胀机有限公司 | The flute profile of high pressure ratio High Pressure Difference twin-screw expander rotor |
| CN113217380A (en) * | 2021-05-24 | 2021-08-06 | 中国船舶重工集团公司第七一一研究所 | Double-screw compressor rotor designed based on intelligent algorithm |
| CN113503255A (en) * | 2021-09-01 | 2021-10-15 | 西漠能源技术（苏州）有限公司 | Rotor end face tooth profile of screw compressor and design method thereof |
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