CN216894894U - Double-screw compressor rotor - Google Patents
Double-screw compressor rotor Download PDFInfo
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- CN216894894U CN216894894U CN202121128196.4U CN202121128196U CN216894894U CN 216894894 U CN216894894 U CN 216894894U CN 202121128196 U CN202121128196 U CN 202121128196U CN 216894894 U CN216894894 U CN 216894894U
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Abstract
The utility model discloses a double-screw compressor rotor, which comprises a female rotor and a male rotor, wherein the meshing line of the female rotor and the male rotor is formed by smoothly connecting eight sections of curves end to end, and the eight sections of curves sequentially comprise an arc section AB, an arc section BC, an elliptical arc section CD, an arc section DE, a cubic spline curve section EF, a cubic spline curve section FG, an arc section GH and an arc section HA; the end face of the female rotor and the end face of the male rotor are respectively formed by connecting eight sections of curves end to end smoothly, and the eight sections of curves are obtained by meshing line conversion respectively. After the scheme is adopted, the male rotor and the female rotor can be optimally meshed in the working process, the tooth curves formed by two adjacent sections are in smooth transition at the connecting point, the number of teeth of the rotor is larger, the rotor can bear larger pressure difference, the utilization coefficient of the area of the rotor is larger, the contact line is shorter, the leakage triangle is smaller, the molded line is in a streamline type, the thermodynamic performance is good, and the working efficiency of the screw compressor is improved.
Description
Technical Field
The utility model relates to a rotor end face tooth profile of a screw compressor, in particular to a rotor profile of a double-screw compressor.
Background
The screw compressor realizes the compression of gas and the transmission of power by means of a pair of screw rotors which do rotary motion in the machine shell. By means of a series of unique advantages of simple structure, good power balance, energy conservation, high efficiency and the like, the screw compressor becomes the fastest-developing volumetric compression machine in recent years, and is widely applied to various industrial fields such as air power, refrigeration and air conditioning, petrochemical industry, process flows, fuel cells and the like. The profile (cross-sectional tooth profile) of a screw rotor, which is a core component, is required to have as large a tooth space volume as possible, good meshing characteristics, and a small aerodynamic loss. The molded lines of the screw rotor are generally formed by connecting multiple sections of curves, the molded lines are complex and asymmetric, and the spiral tooth profile of the screw rotor also has the characteristics of large screw pitch, large helix angle, large tooth profile height and the like, and determines the performance parameters of most parts of the compressor. The screw compressor achieves sealing between rotors by meshing lines, researches are carried out on the aspects of stress deformation, thermal expansion and meshing characteristics of rotor molded lines of the rotors, and a novel efficient rotor molded line is designed on the basis of the research, so that the working efficiency of the double-screw compressor can be improved. And the research is carried out on the aspects of mechanisms such as friction, leakage, heat exchange and the like of the compressor in the operation process, and the optimization design is carried out on different problems, so that the related performance and parameters can be further improved.
Disclosure of Invention
The technical problem to be solved by the utility model is to provide a double-screw compressor rotor which can realize optimal meshing between a male rotor and a female rotor in the working process, the adjacent two sections of formed tooth curves are in smooth transition at a connecting point, the number of teeth of the rotor is larger, larger pressure difference can be borne, the utilization coefficient of the area of the rotor is larger, the contact line is shorter, the leakage triangle is smaller, the molded line is in a streamline shape, and the double-screw compressor rotor has good thermodynamic performance, thereby improving the working efficiency of the double-screw compressor, improving the precision in the processing process and prolonging the service life of a cutter.
The rotor of the double-screw compressor comprises a female rotor and a male rotor, wherein the meshing line of the female rotor and the male rotor is formed by smoothly connecting eight sections of curves end to end, and the eight sections of curves sequentially comprise an arc section AB, an arc section BC, an elliptical arc section CD, an arc section DE, a cubic spline curve section EF, a cubic spline curve section FG, an arc section GH and an arc section HA; each profile of tooth of the terminal surface of negative rotor and the terminal surface of positive rotor forms by eight sections curve head and the tail smooth connection, wherein: the tooth curve of each tooth type on the end surface 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 and a curve section H2I2 which are connected in sequence, and the tooth curve of each tooth type on the end surface 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 and a curve section H1I 1; curve segment A2B2, curve segment B2C2, curve segment C2D2, curve segment D2E2, curve segment E2F2, curve segment F2G2, curve segment G2H2 and curve segment H2I2 are obtained by conversion from the meshing line coordinate system to the female rotor coordinate system of arc segment AB, arc segment BC, elliptical arc segment CD, arc segment DE, cubic spline curve segment EF, cubic spline curve segment FG, arc segment GH and arc segment HA, respectively, and curve segment A1B1, curve segment B1C1, curve segment C1D1, curve segment D1E1, curve segment E1F1, curve segment F1G1, curve segment G1H1 and curve segment H1I1 are obtained by conversion from the meshing line coordinate system to the male rotor coordinate system of arc segment AB, arc segment BC, spline segment CD, arc segment DE, cubic spline segment EF, cubic curve segment FG, rotor segment and GH.
Compared with other tooth types, the rotor tooth type of the double-screw compressor provided by the embodiment of the utility model at least has the following advantages and characteristics:
1. by optimizing the meshing line, the female rotor adopts a more proper tooth depth radius, the tooth area utilization coefficient reaches 57 percent, the female rotor is very suitable for a large-flow compressor, and simultaneously, the larger tooth thickness is reserved, so that the female rotor reaches a better rigidity condition;
2. the molded line of the female rotor is designed into a streamline type, so that the disturbance resistance of airflow is reduced, the loss is reduced, the noise is reduced, and the operation efficiency of the rotor is improved;
3. the molded line tooth surfaces are smoothly connected, so that the processing and detection are convenient, and the service life of the screw rotor cutter is greatly prolonged;
4. the performance of the double-screw compressor is mainly reflected by the meshing line, and the embodiment of the utility model combines the traditional forward design method with the reverse design method based on the meshing line method, so that the performance of the rotor profile can be better ensured. The meshing line adjustment enables the length of a contact line between the rotors to be short, the leakage triangle is small, the pressure difference born by the compressor of the rotors is improved, the tooth-shaped area is increased, and the efficiency of the screw compressor is improved. The generated meshing profile is optimized by using a neural network algorithm, so that the area of a leakage triangle is reduced as much as possible under the condition that the length of a contact line is relatively small, the leakage of a compressor is reduced to a large extent, and the relative volumetric efficiency is relatively high.
Drawings
FIG. 1 shows a schematic view of a female rotor and a male rotor in mesh with each other according to an embodiment of the utility model.
Figure 2 shows a tooth trace schematic of one embodiment of the female rotor of the present invention.
Figure 3 shows a tooth trace schematic of one embodiment of the male rotor of the present invention.
FIG. 4 shows a schematic view of the meshing lines of the female and male rotors of an embodiment of the present invention.
In the figure: o1 is the axis of the male rotor, O2 is the axis of the female rotor; mj is the pitch circle of the male rotor, R1Is the pitch radius of the male rotor; fj isPitch circle of female rotor, R2Is the pitch circle radius of the female rotor; a is the center distance between two rotors, and A is R1+R2(ii) a O3 is the center of the meshing line arc AB, R3Is the radius of the meshing line arc AB; o4 is the center of meshing line arc BC, R4Is the radius of the meshing line arc BC; o5 is the center of the meshing line elliptical arc CD; o6 is the center of the meshing line arc DE, R6Is the radius of the meshing line arc DE; o7 is the center of mesh line circular arc GH, R7Is the radius of the meshing line arc GH; o8 is the center of the meshing line arc HA, R8Is the radius of the meshing line arc HA.
Detailed Description
The tooth profile of the rotor of the twin-screw compressor according to the utility model is described in detail below with reference to the figures and the specific examples.
Please refer to fig. 1 to 4. The rotor of the twin-screw compressor according to an embodiment of the present invention includes a female rotor F and a male rotor M. The female rotor F and the male rotor M are of bilateral asymmetric tooth type, and the number of teeth on the female rotor F is more than that on the male rotor M. In this embodiment, the ratio of the teeth of the male rotor M to the female rotor F is 4: 6.
As shown in fig. 4, the meshing line between the female rotor F and the male rotor M is formed by smoothly connecting eight curves end to end, and the eight curves sequentially include an arc segment AB, an arc segment BC, an elliptical arc segment CD, an arc segment DE, a cubic spline curve segment EF, a cubic spline curve segment FG, an arc segment GH, and an arc segment HA.
In the present embodiment, in the meshing line of the female rotor F and the male rotor M:
the arc section AB is a section of arc with the radius n1 times the radius of the pitch circle of the female rotor and the O3 inside the pitch circle of the female rotor as the center of a circle, n1 is a positive number which is more than 0.2 and less than or equal to 0.25, the arc section AB is smoothly connected with the arc section HA at the starting point A and is tangentially connected with the arc section BC at the end point B;
the arc segment BC is a segment of arc with the radius n2 times the radius of the pitch circle of the female rotor and the O4 inside the pitch circle of the female rotor as the center of a circle, n2 is a positive number which is more than 0.3 and less than or equal to 0.4, the arc segment BC is smoothly connected with the arc segment AB at the starting point B and is tangentially connected with the elliptical arc segment CD at the terminal point C;
the elliptical arc section CD is a section of elliptical arc with the center of O5 inside the female rotor pitch circle, the major axis of the elliptical arc section CD is n3 times the female rotor pitch circle radius, and the minor axis of the elliptical arc section CD is n4 times the female rotor pitch circle radius; n3 is a positive number greater than 0.6 and less than or equal to 0.8, n4 is a positive number greater than 0.3 and less than or equal to 0.5, and the elliptical arc section CD is smoothly connected with the arc section BC at the starting point C and is tangentially connected with the arc section DE at the end point D;
the circular arc section DE is a circular arc which takes O6 outside a pitch circle of the male rotor as a circle center and has the radius of n5 times of the radius of the pitch circle of the female rotor; n5 is a positive number of 0.05 to 0.1 inclusive; the circular arc section DE is smoothly connected with the elliptical arc section CD at the starting point D and is tangentially connected with the cubic spline curve section EF at the terminal point E;
the cubic spline curve segment EF is smoothly connected with the arc segment DE at the starting point E and is tangentially connected with the cubic spline curve segment FG at the terminal point F;
the cubic spline curve segment FG is smoothly connected with the cubic spline curve segment EF at the starting point F and is tangentially connected with the circular arc segment GH at the terminal point G;
the circular arc segment GH is a circular arc which takes O7 outside the pitch circle of the male rotor as the center of a circle and has the radius of n6 times the radius of the pitch circle of the female rotor; n6 is a positive number greater than 0.5 and less than or equal to 0.7, the arc segment GH is smoothly connected with the cubic spline curve segment FG at the starting point G and is tangentially connected with the arc segment HA at the terminal point H;
the arc section HA is a section of arc which takes O8 outside the pitch circle of the male rotor as the center of a circle and HAs the radius of n7 times the radius of the pitch circle of the female rotor; n7 is a positive number greater than 0.7 and less than or equal to 0.9, and the arc segment HA is smoothly connected with the arc segment GH at the starting point H and is tangentially connected with the arc segment AB at the end point A.
Please refer to fig. 1 to fig. 3. Each tooth type of the terminal surface of negative rotor F and the terminal surface of positive rotor M is formed by eight sections curve head and the tail smooth connection, 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 and a curve section H2I2 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 and a curve section H1I 1.
The tooth-shaped 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 and the curve segment H2I2 on the end surface of the female rotor are respectively obtained by converting an arc segment AB, an arc segment BC, an elliptical arc segment CD, an arc segment DE, a cubic spline curve segment EF, a cubic spline curve segment FG, an arc segment GH and an arc segment HA from a meshing line coordinate system to a female rotor coordinate system, and the formula for converting the meshing line coordinate system to the female rotor coordinate system is as follows:
wherein r is2Is the equation of the female rotor, t, for finding the tooth form coordinate of the female rotorsIs a meshing coordinate parameter, R2Is the radius of the pitch circle of the female rotor, X and Y are the coordinates of the meshing line,
is the angle at which the meshing line changes to the tooth form coordinate of the female rotor.
The tooth-shaped curve section A1B1, the curve section B1C1, the curve section C1D1, the curve section D1E1, the curve section E1F1, the curve section F1G1, the curve section G1H1 and the curve section H1I1 of the end surface of the male rotor are respectively obtained by converting an arc section AB, an arc section BC, an elliptical arc section CD, an arc section DE, a cubic spline curve section EF, a cubic spline curve section FG, an arc section GH and an arc section HA from a meshing line coordinate system to a male rotor coordinate system. The equation for converting the meshing line coordinate system into the male rotor coordinate system is as follows:
wherein r is1Is the male rotor equation, t, for finding the tooth form coordinate of the male rotorsIs a meshing coordinate parameter, R1Is the radius of the pitch circle of the male rotor, X and Y are the coordinates of the meshing line,
is the angle at which the meshing line changes to the male rotor tooth coordinate.
Thus, the end face tooth shapes of the male and female rotors of the screw compressor are completely made.
Claims (4)
1. The rotor of the double-screw compressor comprises a female rotor and a male rotor, and is characterized in that the meshing line of the female rotor and the male rotor is formed by smoothly connecting eight sections of curves end to end, and the eight sections of curves sequentially comprise an arc section AB, an arc section BC, an elliptical arc section CD, an arc section DE, a cubic spline curve section EF, a cubic spline curve section FG, an arc section GH and an arc section HA;
the terminal surface of negative rotor and each flute profile of the terminal surface of positive rotor form by eight sections curve end to end smooth connection, wherein: the tooth curves of the tooth types on the end surface of the female 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, a curve section G2H2 and a curve section H2I2 which are connected in sequence, and 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 curve section D1E1, a curve section E1F1, a curve section F1G1, a curve section G1H1 and a curve section H1I 1;
curve segment A2B2, curve segment B2C2, curve segment C2D2, curve segment D2E2, curve segment E2F2, curve segment F2G2, curve segment G2H2 and curve segment H2I2 are obtained by conversion from the meshing line coordinate system to the female rotor coordinate system of arc segment AB, arc segment BC, elliptical arc segment CD, arc segment DE, cubic spline curve segment EF, cubic spline curve segment FG, arc segment GH and arc segment HA, respectively, and curve segment A1B1, curve segment B1C1, curve segment C1D1, curve segment D1E1, curve segment E1F1, curve segment F1G1, curve segment G1H1 and curve segment H1I1 are obtained by conversion from the meshing line coordinate system to the male rotor coordinate system of arc segment AB, arc segment BC, spline segment CD, arc segment DE, cubic spline segment EF, cubic curve segment FG, rotor segment and GH.
2. The rotor of a twin-screw compressor, as set forth in claim 1, characterized in that in the meshing line of the female rotor and the male rotor:
the arc section AB is a section of arc with the radius n1 times the radius of the pitch circle of the female rotor and the O3 inside the pitch circle of the female rotor as the center of a circle, n1 is a positive number which is more than 0.2 and less than or equal to 0.25, the arc section AB is smoothly connected with the arc section HA at the starting point A and is tangentially connected with the arc section BC at the end point B;
the arc segment BC is a segment of arc with the radius n2 times the radius of the pitch circle of the female rotor and the O4 inside the pitch circle of the female rotor as the center of a circle, n2 is a positive number which is more than 0.3 and less than or equal to 0.4, the arc segment BC is smoothly connected with the arc segment AB at the starting point B and is tangentially connected with the elliptical arc segment CD at the terminal point C;
the elliptical arc section CD is a section of elliptical arc with the center of O5 inside the female rotor pitch circle, the major axis of the elliptical arc section CD is n3 times the female rotor pitch circle radius, and the minor axis of the elliptical arc section CD is n4 times the female rotor pitch circle radius; n3 is a positive number greater than 0.6 and less than or equal to 0.8, n4 is a positive number greater than 0.3 and less than or equal to 0.5, and the elliptical arc section CD is smoothly connected with the arc section BC at the starting point C and is tangentially connected with the arc section DE at the end point D;
the circular arc section DE is a circular arc which takes O6 outside a pitch circle of the male rotor as a circle center and has the radius of n5 times of the radius of the pitch circle of the female rotor; n5 is a positive number of 0.1 to 0.05 inclusive; the circular arc section DE is smoothly connected with the elliptical arc section CD at the starting point D and is tangentially connected with the cubic spline curve section EF at the end point E;
the cubic spline curve segment EF is smoothly connected with the arc segment DE at the starting point E and is tangentially connected with the cubic spline curve segment FG at the terminal point F;
the cubic spline curve segment FG is smoothly connected with the cubic spline curve segment EF at the starting point F and is tangentially connected with the circular arc segment GH at the terminal point G;
the circular arc segment GH is a circular arc which takes O7 outside a pitch circle of the male rotor as a circle center and has the radius of n6 times of the pitch circle radius of the female rotor; n6 is a positive number greater than 0.5 and less than or equal to 0.7, the arc segment GH is smoothly connected with the cubic spline curve segment FG at the starting point G and is tangentially connected with the arc segment HA at the terminal point H;
the arc section HA is a section of arc which takes O8 outside the pitch circle of the male rotor as the center of a circle and HAs the radius of n7 times the radius of the pitch circle of the female rotor; n7 is a positive number greater than 0.7 and less than or equal to 0.9, and the arc segment HA is smoothly connected with the arc segment GH at the starting point H and is tangentially connected with the arc segment AB at the end point A.
3. The rotor of a twin-screw compressor, as set forth in claim 1, wherein the rotor profiles of said female rotor and said male rotor are asymmetrical, and the number of teeth on the female rotor is greater than the number of teeth on the male rotor.
4. The rotor of a twin-screw compressor according to claim 1, characterized in that the gear ratio of the male rotor to the female rotor is 4: 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121128196.4U CN216894894U (en) | 2021-05-24 | 2021-05-24 | Double-screw compressor rotor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121128196.4U CN216894894U (en) | 2021-05-24 | 2021-05-24 | Double-screw compressor rotor |
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| CN216894894U true CN216894894U (en) | 2022-07-05 |
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| CN202121128196.4U Active CN216894894U (en) | 2021-05-24 | 2021-05-24 | Double-screw compressor rotor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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2021
- 2021-05-24 CN CN202121128196.4U patent/CN216894894U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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Address after: 201108 3111 Huaning Road, Minhang District, Shanghai Patentee after: The 711 Research Institute of China Shipbuilding Corp. Patentee after: SHANGHAI QIYAO SCREW MACHINERY Co.,Ltd. Address before: 201108 3111 Huaning Road, Minhang District, Shanghai Patentee before: Shanghai Marine Diesel Engine Research Institute Patentee before: SHANGHAI QIYAO SCREW MACHINERY Co.,Ltd. |
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| CP01 | Change in the name or title of a patent holder |