CN216157896U - Tooth profile of double-screw compressor rotor - Google Patents
Tooth profile of double-screw compressor rotor Download PDFInfo
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- CN216157896U CN216157896U CN202121108393.XU CN202121108393U CN216157896U CN 216157896 U CN216157896 U CN 216157896U CN 202121108393 U CN202121108393 U CN 202121108393U CN 216157896 U CN216157896 U CN 216157896U
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Abstract
The utility model discloses a tooth profile of a rotor of a double-screw compressor, wherein the double-screw compressor comprises a female rotor and a male rotor and is characterized in that each tooth profile of the end surface of the female rotor is formed by smoothly connecting six sections of curves end to end, each tooth profile of the end surface of the male rotor is formed by smoothly connecting six sections of curves end to end, and the tooth profile of the end surface of the male rotor comprises an arc line, an arc envelope curve and an elliptical envelope curve; the tooth curve of the end face of the female rotor comprises an arc line, an arc envelope line and an elliptic arc line. After the technical 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 utilization coefficient of the rotor area is large, the contact line is short, the leakage triangle is relatively small, the molded line is in a streamline shape, and the compressor has good thermodynamic performance, so that 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 has the advantages of high reliability, good power balance, less leakage, high efficiency and the like, and is widely applied to the industries of refrigeration, mines, petrifaction and the like. The rotor of the double-screw compressor has a crucial influence on the performance of the whole compressor, and the rotor profile directly determines the performance of the rotor of the double-screw compressor, so that the optimal design of the double-screw compressor depends on the design of the rotor profile. The rotor profiles of the existing foreign twin-screw compressor with excellent performance mainly comprise a German GHH profile, a Japanese Hitachi profile and a Swedish SRM-D asymmetric profile, which do not reach the optimal balance to the maximum extent in the aspects of geometrical characteristics such as small leakage triangle area, large tooth space area, short contact line and the like, and the optimization design of the rotor profiles can be realized only by improving the geometrical properties in the aspects, so that the internal flow area of the twin-screw compressor is large, the leakage is small, on the other hand, the internal gas pulsation generated by the relative motion of a female rotor and a male rotor is small, the noise in the operation of the compressor is low, and the working efficiency of the twin-screw compressor is improved.
Disclosure of Invention
The technical problem to be solved by the utility model is to provide a screw compressor rotor tooth profile, and the compressor with the tooth profile can realize optimal meshing between a male rotor and a female rotor in the working process, two adjacent sections form tooth curves which are in smooth transition at a connecting point, the number of the rotor teeth is larger, larger pressure difference can be borne, the utilization coefficient of the rotor area is larger, the contact line is shorter, the leakage triangle is relatively smaller, the female rotor profile is streamline, and the pulsation of gas in the compressor is reduced, so that the working efficiency of the screw compressor is improved.
According to the tooth profile of the rotor of the twin-screw compressor provided by the embodiment of the utility model, the twin-screw compressor comprises a female rotor and a male rotor, and is characterized in that each tooth profile of the end surface of the female rotor is formed by smoothly connecting six sections of curves end to end, and each tooth profile of the end surface of the male rotor is formed by smoothly connecting six sections of curves end to end, wherein: the tooth curve of the end face of the male rotor comprises an arc line, an arc envelope line and an elliptic envelope line; the tooth curve of the end face of the female rotor comprises an arc line, an arc envelope line and an elliptic arc line.
The embodiment of the utility model designs a novel screw compressor rotor tooth profile by combining a geometric method and a particle swarm algorithm, and compared with other molded lines, the rotor molded line has the following advantages:
1. the molded lines of the female rotor in the embodiment of the utility model are designed into a streamline shape, so that the disturbance resistance of airflow is reduced, the loss is reduced, the noise is reduced, the operation efficiency of the rotor is improved, the rotor expands under the high-temperature condition, the gap between the female rotor and the male rotor is not uniform, the tooth profile of the female rotor consists of an arc envelope line, an arc and an elliptic arc, and the adjustment is easy according to the inconsistency of the gap;
2. the female rotor of the embodiment of the utility model adopts a proper tooth depth radius, so that the female rotor is very suitable for a large-flow compressor, and simultaneously keeps a deep tooth thickness, so that the rotor achieves a good rigidity condition;
3. the embodiment of the utility model realizes the optimization of the rotor profile, reduces the area of the leakage triangle as much as possible under the condition that the length of the contact line is smaller, reduces the leakage of the compressor to a greater extent, and has higher relative volumetric efficiency.
Drawings
FIG. 1 is a schematic view of an example of female and male rotors of the present invention as they intermesh.
Fig. 2 is a schematic view of the tooth profile of the female rotor of the present invention.
Fig. 3 is a schematic view of the tooth profile of the male rotor 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, R1 is the pitch circle radius of the male rotor; fj is the pitch circle of the female rotor, R2 is the pitch circle radius of the female rotor; a is the center-to-center distance of the two rotors, a = R1+ R2; o3 is the center of the female rotor arc A2B2, R3 is the radius of the female rotor arc A2B 2; o4 is the center of the female rotor arc B2C2, R4 is the radius of the female rotor arc B2C 2; o5 is the center of the female rotor elliptical arc C2D 2; o6 is the center of female rotor arc E2a2, R6 is the radius of female rotor arc E2a 2; o7 is the center of the female rotor arc F2E2, R7 is the radius of the female rotor arc E2F 2; o8 is the center of the male rotor arc G1F1 and R8 is the radius of the male rotor arc G1F 1.
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 3. The rotor tooth shapes of the female rotor F and the male rotor M of the double-screw compressor are bilateral asymmetric, 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: 5.
According to the tooth profile of the rotor of the dry type twin-screw compressor provided by the embodiment of the utility model, the twin-screw compressor comprises a female rotor F and a male rotor M. Each profile of tooth of the terminal surface of negative rotor F is formed by six sections curve end to end smooth connections, and each profile of the terminal surface of positive rotor M is formed by six sections curve end to end smooth connections, wherein: the tooth curve of the end face of the male rotor comprises an arc line, an arc envelope line and an elliptic envelope line; the tooth curve of the end face of the female rotor comprises an arc line, an arc envelope line and an elliptic arc line. In this embodiment: the tooth curves of the tooth types on the end surface of the female rotor comprise the following smoothly connected tooth curves in sequence: an arc envelope G2F2, an arc F2E2, an arc E2A2, an arc A2B2, an arc B2C2, and an elliptical arc C2D 2; the tooth curves of the tooth types of the male rotor comprise the following smoothly connected sequences: an arc G1F1, an arc envelope F1E1, an arc envelope E1A1, an arc envelope A1B1, an arc envelope B1C1, and an elliptical arc envelope C1D 1.
The circular arc envelope G2F2 of each tooth type of the female rotor is a section of circular arc envelope of a track formed by the motion of a female rotor pitch circle relative to a male rotor circular arc G1F1 when the female rotor pitch circle rolls along a male rotor pitch circle; each tooth type circular arc G1F1 of the male rotor is a section of circular arc which takes O8 outside a female rotor pitch circle as a center and has the radius n7 times the radius of the male rotor pitch circle, n7 is a positive number which is more than 0.5 and less than or equal to 0.7, the circular arc G1F1 is smoothly connected with the terminal point of the other adjacent tooth of the male rotor at the starting point G1 and is smoothly connected with an envelope curve F1E1 at the terminal point F1;
each tooth-shaped arc F2E2 of the female rotor is a segment of arc with the radius n1 times the pitch circle radius of the female rotor and the center of O7 outside the pitch circle of the female rotor, wherein n1 is a positive number which is more than 0.5 and less than or equal to 0.7; the arc F2E2 is tangentially connected with the arc envelope G2F2 at the starting point F2 and is smoothly connected with the arc E2A2 at the terminal point E2; the circular arc envelope curve F1E1 of each tooth type of the male rotor is a section of circular arc envelope curve of a track formed by the motion of a male rotor pitch circle relative to a female rotor circular arc F2E2 when the male rotor pitch circle rolls along a female rotor pitch circle;
each tooth-shaped circular arc E2A2 of the female rotor is a section of circular arc with the radius n2 times the pitch circle radius of the female rotor and the center of O6 outside the pitch circle of the male rotor, wherein n2 is a positive number which is more than 0.2 and less than or equal to 0.3; the arc E2A2 is tangentially connected with the arc F2E2 at the starting point E2 and is smoothly connected with the arc A2B2 at the terminal point A2; the circular arc envelope line E1A1 of each tooth type of the male rotor is a section of circular arc envelope line of a track formed by the motion of a male rotor pitch circle relative to a female rotor circular arc E2A2 when the male rotor pitch circle rolls along a female rotor pitch circle;
each tooth-shaped arc A2B2 of the female rotor is a segment of arc with the radius n3 times the pitch circle radius of the female rotor and the center of O3 in the pitch circle of the female rotor, wherein n3 is a positive number which is more than 0.3 and less than or equal to 0.6; the arc A2B2 is smoothly connected with the arc E2A2 at the starting point A2 and is tangentially connected with the arc B2C2 at the terminal point B2; the circular arc envelope line A1B1 of each tooth type of the male rotor is a section of circular arc envelope line of a track formed by the motion of a male rotor pitch circle relative to a female rotor circular arc A2B2 when the male rotor pitch circle rolls along a female rotor pitch circle;
each tooth-shaped circular arc B2C2 of the female rotor is a section of circular arc which takes O4 in a pitch circle of the female rotor as the center of a circle and has the radius of n4 times the radius of the pitch circle of the female rotor, and n4 is a positive number which is more than 0.7 and less than or equal to 0.9; the arc B2C2 is smoothly connected with the arc A2B2 at the starting point B2 and is tangentially connected with the elliptical arc C2D2 at the terminal point C2; the circular arc envelope line B1C1 of each tooth type of the male rotor is a section of circular arc envelope line of a track formed by the motion of a male rotor pitch circle relative to a female rotor circular arc B2C2 when the male rotor pitch circle rolls along a female rotor pitch circle;
the elliptical arc C2D2 of each tooth shape of the female rotor is an elliptical arc which takes O5 in the pitch circle of the female rotor as the center, the major axis is n5 times the pitch circle radius of the female rotor, the minor axis is n6 times the pitch circle radius of the female rotor, n5 is a positive number which is more than 0.5 and less than or equal to 0.8, and n6 is a positive number which is more than 0.3 and less than or equal to 0.5; the elliptic arc C2D2 is smoothly connected with the circular arc B2C2 at the starting point C2 and is tangentially connected with the starting point of the adjacent other tooth of the female rotor at the terminal point D2; the elliptical arc envelope C1D1 of each tooth of the male rotor is an elliptical arc envelope of a track formed by the motion of the male rotor pitch circle relative to the female rotor elliptical arc C2D2 as it rolls along the female rotor pitch circle.
Compared with the prior art, the tooth shapes of the end surfaces of the female rotor and the male rotor in the embodiment of the utility model have the advantages that under the condition that the length of the contact line is reduced by 11.67%, the area utilization coefficient is improved by 8.54%, the area of the leakage triangle is reduced by 4.35%, so that the tooth shape area utilization coefficient is increased, the leakage of the rotor is reduced, the pressure difference which can be borne by the compressor is improved, and the tooth shapes are particularly suitable for the working conditions of high temperature and large flow.
Claims (5)
1. The tooth profile of double screw compressor rotor, double screw compressor includes negative rotor and positive rotor, its characterized in that, each tooth profile of the terminal surface of negative rotor forms by six sections curve end to end smooth connection, each tooth profile of the terminal surface of positive rotor forms by six sections curve end to end smooth connection, wherein: the tooth curve of the end face of the male rotor comprises an arc line, an arc envelope line and an elliptic envelope line; the tooth curve of the end face of the female rotor comprises an arc line, an arc envelope line and an elliptic arc line;
the tooth curves of the tooth types of the female rotor comprise the following smoothly connected sequences: an arc envelope G2F2, an arc F2E2, an arc E2A2, an arc A2B2, an arc B2C2, and an elliptical arc C2D 2;
the tooth curves of the tooth types of the male rotor comprise the following smoothly connected sequences: an arc G1F1, an arc envelope F1E1, an arc envelope E1A1, an arc envelope A1B1, an arc envelope B1C1, and an elliptical arc envelope C1D 1.
2. Tooth profile of a rotor of a twin-screw compressor, according to claim 1, characterized in that in the tooth profile of each tooth profile of the female rotor:
the arc envelope G2F2 is a segment of arc envelope of a track formed by the motion of the female rotor pitch circle relative to the male rotor arc G1F1 when the female rotor pitch circle rolls along the male rotor pitch circle;
the arc F2E2 is a segment of arc with the radius n1 times the radius of the pitch circle of the female rotor and the O7 outside the pitch circle of the female rotor is used as the center of the circle, and n1 is a positive number which is more than 0.5 and less than or equal to 0.7; the arc F2E2 is tangentially connected with the arc envelope G2F2 at the starting point F2 and is smoothly connected with the arc E2A2 at the terminal point E2;
the arc E2A2 is a segment of arc with the radius n2 times the pitch circle radius of the female rotor and the O6 outside the pitch circle of the male rotor is used as the center of the circle, and n2 is a positive number which is more than 0.2 and less than or equal to 0.3; the arc E2A2 is tangentially connected with the arc F2E2 at the starting point E2 and is smoothly connected with the arc A2B2 at the terminal point A2;
the arc A2B2 is a segment of arc with the radius n3 times the radius of the pitch circle of the female rotor and the center of O3 in the pitch circle of the female rotor, and n3 is a positive number which is more than 0.3 and less than or equal to 0.6; the arc A2B2 is smoothly connected with the arc E2A2 at the starting point A2 and is tangentially connected with the arc B2C2 at the terminal point B2;
the arc B2C2 is a segment of arc which takes O4 in the pitch circle of the female rotor as the center of a circle and has the radius of n4 times the radius of the pitch circle of the female rotor, and n4 is a positive number which is more than 0.7 and less than or equal to 0.9; the arc B2C2 is smoothly connected with the arc A2B2 at the starting point B2 and is tangentially connected with the elliptical arc C2D2 at the terminal point C2;
the elliptic arc C2D2 is an elliptic arc which takes O5 in the pitch circle of the female rotor as the center, the major axis of the elliptic arc is n5 times of the pitch circle radius of the female rotor, the minor axis of the elliptic arc is n6 times of the pitch circle radius of the female rotor, n5 is a positive number which is more than 0.5 and less than or equal to 0.8, and n6 is a positive number which is more than 0.3 and less than or equal to 0.5; the elliptical arc C2D2 smoothly connects with the arc B2C2 at the starting point C2 and tangentially connects with the starting point of another tooth adjacent to the female rotor at the ending point D2.
3. Profile of teeth of a rotor of a twin-screw compressor, according to claim 1 or 2, characterized in that in the profile of teeth of each profile of the male rotor:
the arc G1F1 is a segment of arc which takes O8 outside the pitch circle of the female rotor as the center of a circle and has the radius n7 times the radius of the pitch circle of the male rotor, n7 is a positive number which is more than 0.5 and less than or equal to 0.7, the arc G1F1 is smoothly connected with the terminal point of the other adjacent tooth of the male rotor at the starting point G1 and is smoothly connected with the envelope curve F1E1 at the terminal point F1;
the arc envelope F1E1 is a segment of arc envelope of a track formed by the motion of the male rotor pitch circle relative to the female rotor arc F2E2 when the male rotor pitch circle rolls along the female rotor pitch circle;
the arc envelope line E1A1 is a section of arc envelope line of a track formed by the motion of the male rotor pitch circle relative to the female rotor arc E2A2 when the male rotor pitch circle rolls along the female rotor pitch circle;
the arc envelope line A1B1 is a section of arc envelope line of a track formed by the motion of the male rotor pitch circle relative to the female rotor arc A2B2 when the male rotor pitch circle rolls along the female rotor pitch circle;
the arc envelope B1C1 is a segment of arc envelope of a track formed by the motion of the male rotor pitch circle relative to the female rotor arc B2C2 when the male rotor pitch circle rolls along the female rotor pitch circle;
the elliptical arc envelope C1D1 is an elliptical arc envelope of the trajectory defined by the motion of the male rotor pitch circle relative to the female rotor elliptical arc C2D2 as it rolls along the female rotor pitch circle.
4. The twin screw compressor rotor profile of claim 1, wherein the rotor profiles of the female and male rotors are bilaterally asymmetrical with a greater number of teeth on the female rotor than on the male rotor.
5. The twin-screw compressor rotor profile according to claim 1, wherein the ratio of the number of teeth of the male rotor to the female rotor is 4: 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121108393.XU CN216157896U (en) | 2021-05-24 | 2021-05-24 | Tooth profile of double-screw compressor rotor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121108393.XU CN216157896U (en) | 2021-05-24 | 2021-05-24 | Tooth profile of double-screw compressor rotor |
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| Publication Number | Publication Date |
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| CN216157896U true CN216157896U (en) | 2022-04-01 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202121108393.XU Active CN216157896U (en) | 2021-05-24 | 2021-05-24 | Tooth profile of double-screw compressor rotor |
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- 2021-05-24 CN CN202121108393.XU patent/CN216157896U/en active Active
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| Date | Code | Title | Description |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20220815 Address after: 201108 Shanghai city Minhang District Huaning Road No. 3111 Patentee after: Shanghai Marine Diesel Engine Research Institute Patentee after: SINOPEC ENGINEERING Inc. Patentee after: SHANGHAI QIYAO SCREW MACHINERY Co.,Ltd. Address before: 201108 Shanghai city Minhang District Huaning Road No. 3111 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 | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 201108 Shanghai city Minhang District Huaning Road No. 3111 Patentee after: The 711 Research Institute of China Shipbuilding Corp. Patentee after: SINOPEC ENGINEERING Inc. Patentee after: SHANGHAI QIYAO SCREW MACHINERY Co.,Ltd. Address before: 201108 Shanghai city Minhang District Huaning Road No. 3111 Patentee before: Shanghai Marine Diesel Engine Research Institute Patentee before: SINOPEC ENGINEERING Inc. Patentee before: SHANGHAI QIYAO SCREW MACHINERY Co.,Ltd. |