CN103982425B - A kind of flute profile of dry type double-screw compressor rotor - Google Patents
A kind of flute profile of dry type double-screw compressor rotor Download PDFInfo
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- CN103982425B CN103982425B CN201410217700.6A CN201410217700A CN103982425B CN 103982425 B CN103982425 B CN 103982425B CN 201410217700 A CN201410217700 A CN 201410217700A CN 103982425 B CN103982425 B CN 103982425B
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Abstract
The invention discloses the flute profile of a kind of dry type double-screw compressor rotor, described dry type double-screw compressor includes female rotor and male rotor, it is characterized in that, each flute profile of the end face of female rotor is smoothly connected by eight sections of conic section head and the tail and forms, each flute profile of the end face of male rotor is smoothly connected by seven sections of curve head and the tail and forms, wherein: the tooth curve of male rotor end face includes circular arc line and arc envelope line; The tooth curve of female rotor end face includes circular arc line, arc envelope line and cycloid. After adopting technique scheme, owing to male rotor and female rotor can be made to realize optimal engagement in the course of the work, adjacent two sections of composition tooth curves smoothly transit at junction point place, and rotor contact line is comparatively short, and leakage triangle is relatively small, molded line becomes streamlined, aerodynamic drag is little, has excellent compressor heat mechanical property, thus improving the work efficiency of compressor, and in the course of processing, improve precision, extend the life-span of cutter.
Description
Technical field
The present invention relates to the rotor end-face flute profile of helical-lobe compressor, particularly relate to the molded lines of rotor of a kind of dry type double-screw compressor.
Background technology
Helical-lobe compressor belongs to rotary type displacement equipment, can under relatively larger pressure with range of flow, keep operating under efficient state, molded lines of rotor of helical lobe compressor is the most critical factor affecting compressor performance, the area utilization factor of molded line affects the population structure of compressor, the path of contact of molded line affects volumetric efficiency, and the smooth degree of molded line affects flow efficiency and internal flow noise. In recent years, the development of Compressors in Abroad is quickly, its application constantly expands, especially prominent is, the yield of helical-lobe compressor occupy the Japanese kobe steel that the world is the first, and the adiabatic efficiency of its new tooth improves 10��20% than originally, it is seen that it is very big that compressor efficiency is improved by the design of compressor drum, therefore improving rotor design is that compressor enterprise saves the energy, increases economic efficiency and provides reasonable approach. But, the composition tooth curve of tradition molded line generally there are point, straight line etc., is not easy to processing, it is easy to causes that tooth surface abrasion is fast, and cutter leakage in straight line place is relatively big, and affects detection and the processing of rotor.
Summary of the invention
It is an object of the invention to: be combined, with algebraically up conversion method, the flute profile developing a kind of Novel dry rotor of helical lobe compressor by the vector method of mathematics, and draw out cutter, wherein flute profile includes male rotor and meshed female rotor, their flute profile curve is by circular arc, cycloid and arc envelope line are formed by connecting, there is the compressor of this flute profile, owing to male rotor and female rotor can be made to realize optimal engagement in the course of the work, adjacent two sections of composition tooth curves smoothly transit at junction point place, rotor contact line is comparatively short, leakage triangle is relatively small, molded line becomes streamlined, aerodynamic drag is little, there is excellent compressor heat mechanical property, thus improving the work efficiency of compressor, and in the course of processing, improve precision, extend the life-span of cutter.
For achieving the above object: the technical solution adopted in the present invention is: the flute profile of a kind of dry type double-screw compressor rotor, described dry type double-screw compressor includes female rotor and male rotor, it is characterized in that, each flute profile of the end face of female rotor is smoothly connected by eight sections of conic section head and the tail and forms, each flute profile of the end face of male rotor is smoothly connected by seven sections of curve head and the tail and forms, wherein: the tooth curve of male rotor end face includes circular arc line and arc envelope line;The tooth curve of female rotor end face includes circular arc line, arc envelope line and cycloid.
The present invention adopts vector method to be combined with algebraic transformation method and develops a kind of novel screw compressor rotor flute profile, and this molded lines of rotor is compared other molded line and had the advantage that
1. have employed relatively larger tooth depth radius due to the female rotor of the present invention, flute profile area utilization factor has reached 56%, is very suitable for the mesolow dry screw compressor than big flow;
2., owing to the Profile Design of female rotor becomes streamlined, reduce the disturbance resistance of air-flow, decrease loss, reduce noise, improve the operational efficiency of rotor;
3. it is smoothly connected between the molded line flank of tooth, without cusp on molded line, it is simple to adopt gear hobbing processing and detection so that cutter life is greatly increased;
4. the front flank of tooth of this flute profile have employed circular arc, and the rear flank of tooth have employed circular arc and arc envelope line and cycloid so that contact wire is relatively short, so reveals triangle smaller, so that sealing is better.
Accompanying drawing explanation
Fig. 1 is a kind of example of female rotor of the present invention and the male rotor schematic diagram when engaging each other.
Fig. 2 is the flute profile line schematic diagram of female rotor of the present invention.
Fig. 3 is the flute profile line schematic diagram of male rotor of the present invention.
In figure: O1 is the axle center of male rotor, O2 is the axle center of female rotor; R1 is the radius of the outside circle of male rotor, and R2 is the radius of female rotor outside circle; O3 is node; R1j is the pitch radius of male rotor; R2j is the pitch radius of female rotor, R2j=R2; A is the centre-to-centre spacing of two rotors, A=R1j+R2j; O4 is the center of circle of female rotor circular arc C 2D2, and R4 is the radius of female rotor circular arc C 2D2; O5 is the center of circle of female rotor circular arc E2F2, and R5 is the radius of female rotor circular arc E2F2; O6 is the center of circle of female rotor circular arc F2G2, and R6 is the radius of female rotor circular arc F2G2; O7 is the center of circle of female rotor circular arc H2L2, and R7 is the radius of female rotor circular arc H2L2; O3 is the center of circle of female rotor pin tooth circular arc A2B2, and R3 is female rotor pin tooth circular arc A2B2 and the radius of male rotor pin tooth circular arc A1B1, equal to the height of male rotor fully teeth height; O8 is the center of circle of male rotor circular arc C 1D1, and R8 is the radius of male rotor circular arc C 1D1; O9 is the center of circle of male rotor circular arc E1F1, and R9 is the radius of male rotor circular arc E1F1; O10 is the center of circle of male rotor circular arc A1H1, and R10 is the radius of male rotor circular arc A1H1; O3 is male rotor pin tooth circular arc A1B1 and the center of circle of female rotor pin tooth circular arc A2B2, and R3 is female rotor pin tooth circular arc A2B2 and the radius of male rotor pin tooth circular arc A1B1, equal to the height of male rotor fully teeth height.
Detailed description of the invention
Below in conjunction with accompanying drawing, the flute profile of dry type double-screw compressor rotor of the present invention is elaborated.
Refer to Fig. 1-Fig. 3. The rotor flute profile of the female rotor F and male rotor M of the dry type double-screw compressor of the present invention is asymmetrical type, and the number of teeth on female rotor F is more than the number of teeth on male rotor M. In the present embodiment, the gear ratio of male rotor M and female rotor F is 4:6.
The flute profile of dry type double-screw compressor rotor according to an embodiment of the invention, described dry type double-screw compressor includes female rotor F and male rotor M. Each flute profile of the end face of female rotor F is smoothly connected by eight sections of conic section head and the tail and forms, and each flute profile of the end face of male rotor M is smoothly connected by seven sections of curve head and the tail and forms, wherein: the tooth curve of male rotor end face includes circular arc line and arc envelope line; The tooth curve of female rotor end face includes circular arc line, arc envelope line and cycloid. In the present embodiment: eight sections of curves of each flute profile of female rotor include what order was smoothly connected: pin tooth circular arc A2B2, cycloid B2C2, circular arc C 2D2, arc envelope line D2E2, circular arc E2F2, circular arc F2G2, arc envelope line A2H2 and circular arc H2L2;Seven sections of curves of each flute profile of male rotor include what order was smoothly connected: pin tooth circular arc A1B1, arc envelope line B1C1, circular arc C 1D1, arc envelope line D1E1, circular arc E1F1, circular arc A1H1 and arc envelope line H1L1.
Please refer to Fig. 2. In the tooth curve of each flute profile of female rotor:
Circular arc A2B2 is with O3 for the center of circle, and R3 is one section of pin tooth circular arc of radius;
Cycloid B2C2 is point gearing epicycloid, the B1 point on male rotor pitch circle make pure rolling outside female rotor pitch circle and formed;
Circular arc C 2D2 be with the O4 within female rotor pitch circle be the center of circle, with the R4 one section of circular arc formed for radius; Radius R4 is n1 times of female rotor pitch radius, and n1 is the positive number more than 0.1, less than or equal to 0.4; Circular arc C 2D2 is smoothly connected at starting point C2 place and arc envelope line B2C2, tangent with female rotor arc envelope line D2E2 at terminal D2 place is connected;
Arc envelope line D2E2 is by female rotor pitch circle when rolling along male rotor pitch circle, one section of arc envelope line of the track that relative male rotor C1D1 circular motion is formed;
Circular arc E2F2 be with the O5 within female rotor pitch circle be the center of circle, with the R5 one section of circular arc formed for radius; Radius R5 is n2 times of female rotor pitch radius, and n2 is the positive number more than 0.1, less than or equal to 0.2; Circular arc E2F2 is smoothly connected at starting point E2 place and arc envelope line D2E2, tangent with female rotor circular arc F2G2 at terminal F2 place is connected;
Circular arc F2G2 be with the O6 within female rotor pitch circle be the center of circle, with the R6 one section of circular arc formed for radius; Radius R6 is n3 times of female rotor pitch radius, and n3 is the positive number more than 1, less than or equal to 2; Circular arc F2G2 is smoothly connected with circular arc E2F2 at starting point F2 place, and the terminal at terminal G2 place another tooth adjacent with this female rotor is smoothly connected;
Arc envelope line A2H2 is by female rotor pitch circle when rolling along male rotor pitch circle, one section of arc envelope line of the track that relative male rotor A1H1 circular motion is formed;
Circular arc H2L2 be with the O7 within female rotor pitch circle be the center of circle, with the R7 one section of circular arc formed for radius; Radius R7 is n4 times of female rotor pitch radius, and n4 is the positive number more than 0.1, less than or equal to 0.3; Circular arc H2L2 is smoothly connected with arc envelope line A2H2 at starting point H2 place, and the terminal at terminal L2 place another tooth adjacent with this female rotor is smoothly connected.
Please refer to Fig. 3. In the tooth curve of each flute profile of male rotor:
Circular arc A1B1 is with O3 for the center of circle, and R3 is one section of pin tooth circular arc of radius;
Arc envelope line B1C1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor C2D2 circular motion is formed;
Circular arc C 1D1 be with the O8 within male rotor pitch circle be the center of circle, with the R8 one section of circular arc formed for radius; Radius R8 is n5 times of male rotor pitch radius, and n5 is the positive number more than 0.3, less than or equal to 0.5; Circular arc C 1D1 is smoothly connected at starting point C1 place and arc envelope line B1C1, tangent with male rotor arc envelope line D1E1 at terminal D1 place is connected;
Arc envelope line D1E1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor E2F2 circular motion is formed;
Circular arc E1F1 be with the O9 within male rotor pitch circle be the center of circle, with the R9 one section of circular arc formed for radius; Radius R9 is n6 times of male rotor pitch radius, and n6 is the positive number more than 0, less than or equal to 0.1; Circular arc E1F1 is smoothly connected with arc envelope line D1E1 at starting point E1 place, and the terminal at terminal F1 place another tooth adjacent with this male rotor is smoothly connected;
Circular arc A1H1 be with the O10 within male rotor pitch circle be the center of circle, with the R10 one section of circular arc formed for radius; Radius R10 is n7 times of male rotor pitch radius, and n7 is the positive number more than 0.2, less than or equal to 0.3; Circular arc A1H1 is smoothly connected with circular arc A1B1 at starting point A1 place, is smoothly connected with arc envelope line H1L1 at terminal H1 place;
Arc envelope line H1L1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor H2L2 circular motion is formed.
In the specific implementation:
Described female rotor tooth curve A2B2 circular arc is one section of circular arc that the radius of female rotor pitch circle together decides on the radius of pin tooth circular arc; Male rotor tooth curve A1B1 circular arc is exactly and female rotor tooth curve A2B2 circular arc conjugation, one section of circular arc on male rotor.
Described male rotor tooth curve B1C1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor C2D2 circular motion is formed; Female rotor tooth curve cycloid B2C2 is point gearing epicycloid, the B1 point on male rotor pitch circle make pure rolling outside female rotor pitch circle and formed.
Described female rotor tooth curve C2D2 circular arc be with the O4 within female rotor pitch circle be the center of circle, radius is for the R4 one section of circular arc formed; Circular arc C 2D2 is smoothly connected at starting point and arc envelope line B2C2, is connected terminal is tangent with arc envelope line D2E2; Male rotor tooth curve C1D1 circular arc is with the O8 within male rotor pitch circle for the center of circle, and with the R8 one section of circular arc formed for radius, circular arc C 1D1 is smoothly connected with arc envelope line B1C1 in starting point, tangent with male rotor arc envelope line D1E1 at destination county.
Described male rotor tooth curve arc envelope line D1E1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor E2F2 circular motion is formed; Female rotor tooth curve arc envelope line D2E2 is by female rotor pitch circle when rolling along male rotor pitch circle, one section of arc envelope line of the track that relative male rotor C1D1 circular motion is formed.
Described female rotor tooth curve E2F2 circular arc be with the O5 within female rotor pitch circle be the center of circle, radius for the R5 one section of circular arc formed, circular arc E2F2 is smoothly connected at starting point and arc envelope line D2E2, tangent with female rotor circular arc F2G2 at destination county; Male rotor tooth curve E1F1 circular arc be with the O9 within male rotor pitch circle be the center of circle, with the R9 one section of circular arc formed for radius, circular arc E1F1 is smoothly connected with circular arc D1E1 in starting point, and the terminal at destination county another tooth adjacent with this male rotor is smoothly connected.
Described female rotor tooth curve F2G2 circular arc be with the O6 within female rotor pitch circle be the center of circle, with the R6 one section of circular arc formed for radius, circular arc F2G2 is smoothly connected with circular arc E2F2 in starting point, and the terminal at destination county another tooth adjacent with this female rotor is smoothly connected.
Described male rotor tooth curve A1H1 circular arc be with the O10 within male rotor pitch circle be the center of circle, with the R10 one section of circular arc formed for radius, circular arc A1H1 is smoothly connected with circular arc A1B1 in starting point, is smoothly connected with arc envelope line H1L1 at destination county; Female rotor tooth curve arc envelope line A2H2 is by female rotor pitch circle when rolling along male rotor pitch circle, one section of arc envelope line of the track that relative male rotor A1H1 circular motion is formed.
Described female rotor tooth curve H2L2 circular arc be with the O7 within female rotor pitch circle be the center of circle, with the R7 one section of circular arc formed for radius, circular arc H2L2 is smoothly connected with arc envelope line A2H2 in starting point, and the terminal at destination county another tooth adjacent with this female rotor is smoothly connected;Arc envelope line H1L1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor H2L2 circular motion is formed.
So, the end face tooth type of screw compressor rotor just is made out completely.
Claims (5)
1. the flute profile of a dry type double-screw compressor rotor, described dry type double-screw compressor includes female rotor and male rotor, it is characterized in that, each flute profile of the end face of described female rotor is smoothly connected by eight sections of conic section head and the tail and forms, each flute profile of the end face of described male rotor is smoothly connected by seven sections of curve head and the tail and forms, wherein: the tooth curve of described male rotor end face includes circular arc line and arc envelope line; The tooth curve of described female rotor end face includes circular arc line, arc envelope line and cycloid;
The tooth curve of each flute profile of female rotor includes what order was smoothly connected: pin tooth circular arc A2B2, cycloid B2C2, circular arc C 2D2, arc envelope line D2E2, circular arc E2F2, circular arc F2G2, arc envelope line A2H2 and circular arc H2L2;
The tooth curve of each flute profile of male rotor includes what order was smoothly connected: pin tooth circular arc A1B1, arc envelope line B1C1, circular arc C 1D1, arc envelope line D1E1, circular arc E1F1, circular arc A1H1 and arc envelope line H1L1.
2. the flute profile of a kind of dry type double-screw compressor rotor as claimed in claim 1, it is characterised in that in the tooth curve of each flute profile of described female rotor:
Circular arc A2B2 is with O3 for the center of circle, and R3 is one section of pin tooth circular arc of radius;
Cycloid B2C2 is point gearing epicycloid, the B1 point on male rotor pitch circle make pure rolling outside female rotor pitch circle and formed;
Circular arc C 2D2 be with the O4 within female rotor pitch circle be the center of circle, one section of circular arc being formed for n1 times of female rotor pitch radius of radius; Circular arc C 2D2 is smoothly connected at starting point C2 place and arc envelope line B2C2, tangent with female rotor arc envelope line D2E2 at terminal D2 place is connected, and n1 is the positive number more than 0.1, less than or equal to 0.4;
Arc envelope line D2E2 is by female rotor pitch circle when rolling along male rotor pitch circle, one section of arc envelope line of the track that relative male rotor C1D1 circular motion is formed;
Circular arc E2F2 be with the O5 within female rotor pitch circle be the center of circle, one section of circular arc being formed for n2 times of female rotor pitch radius of radius; Circular arc E2F2 is smoothly connected at starting point E2 place and arc envelope line D2E2, tangent with female rotor circular arc F2G2 at terminal F2 place is connected, and n2 is the positive number more than 0.1, less than or equal to 0.2;
Circular arc F2G2 be with the O6 within female rotor pitch circle be the center of circle, one section of circular arc being formed for n3 times of female rotor pitch radius of radius; Circular arc F2G2 is smoothly connected with circular arc E2F2 at starting point F2 place, and the terminal at terminal G2 place another tooth adjacent with this female rotor is smoothly connected, and n3 is the positive number more than 1, less than or equal to 2;
Arc envelope line A2H2 is by female rotor pitch circle when rolling along male rotor pitch circle, one section of arc envelope line of the track that relative male rotor A1H1 circular motion is formed;
Circular arc H2L2 be with the O7 within female rotor pitch circle be the center of circle, one section of circular arc being formed for n4 times of female rotor pitch radius of radius, circular arc H2L2 is smoothly connected with arc envelope line A2H2 at starting point H2 place, terminal at terminal L2 place another tooth adjacent with this female rotor is smoothly connected, and n4 is the positive number more than 0.1, less than or equal to 0.3.
3. the flute profile of a kind of dry type double-screw compressor rotor as claimed in claim 1, it is characterised in that in the tooth curve of each flute profile of described male rotor:
Circular arc A1B1 is with O3 for the center of circle, and R3 is one section of pin tooth circular arc of radius;
Arc envelope line B1C1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor C2D2 circular motion is formed;
Circular arc C 1D1 be with the O8 within male rotor pitch circle be the center of circle, one section of circular arc being formed for n5 times of male rotor pitch radius of radius; Circular arc C 1D1 is smoothly connected at starting point C1 place and arc envelope line B1C1, tangent with male rotor arc envelope line D1E1 at terminal D1 place is connected, and n5 is the positive number more than 0.3, less than or equal to 0.5;
Arc envelope line D1E1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor E2F2 circular motion is formed;
Circular arc E1F1 be with the O9 within male rotor pitch circle be the center of circle, one section of circular arc being formed for n6 times of male rotor pitch radius of radius; Circular arc E1F1 is smoothly connected with arc envelope line D1E1 at starting point E1 place, and the terminal at terminal F1 place another tooth adjacent with this male rotor is smoothly connected, and n6 is the positive number more than 0, less than or equal to 0.1;
Circular arc A1H1 be with the O10 within male rotor pitch circle be the center of circle, one section of circular arc being formed for n7 times of male rotor pitch radius of radius; Circular arc A1H1 is smoothly connected with circular arc A1B1 at starting point A1 place, is smoothly connected with arc envelope line H1L1 at terminal H1 place, and n7 is the positive number more than 0.2, less than or equal to 0.3;
Arc envelope line H1L1 is by male rotor pitch circle when rolling along female rotor pitch circle, one section of arc envelope line of the track that relative female rotor H2L2 circular motion is formed.
4. the flute profile of a kind of dry type double-screw compressor rotor as claimed in claim 1, it is characterised in that the rotor flute profile of described female rotor and male rotor is asymmetrical type, and the number of teeth on female rotor is more than the number of teeth on male rotor.
5. the flute profile of a kind of dry type double-screw compressor rotor as claimed in claim 4, it is characterised in that the gear ratio of described male rotor and female rotor is 4:6.
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| CN201410217700.6A CN103982425B (en) | 2014-05-20 | 2014-05-20 | A kind of flute profile of dry type double-screw compressor rotor |
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| CN201410217700.6A CN103982425B (en) | 2014-05-20 | 2014-05-20 | A kind of flute profile of dry type double-screw compressor rotor |
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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 |
| 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 |
| CN114320911A (en) * | 2021-12-23 | 2022-04-12 | 珠海格力电器股份有限公司 | Tooth profile curve of a pair of male and female rotors, male and female rotors and screw compressor |
| CN114320912B (en) * | 2021-12-23 | 2023-11-21 | 湖南慧风流体科技有限公司 | Double-screw double-side asymmetric rotor molded line composed of nine-section tooth curves |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US3472445A (en) * | 1968-04-08 | 1969-10-14 | Arthur E Brown | Rotary positive displacement machines |
| ZA794573B (en) * | 1978-09-28 | 1980-08-27 | A Brown | Rotary positive displacement machines |
| DE10103775B4 (en) * | 2001-01-27 | 2005-07-14 | Danfoss A/S | Method and scroll compressor for compressing a compressible medium |
| CN203321827U (en) * | 2013-05-31 | 2013-12-04 | 上海齐耀螺杆机械有限公司 | High-efficiency double screw rod compressor rotor line |
| CN203384049U (en) * | 2013-07-03 | 2014-01-08 | 上海齐耀螺杆机械有限公司 | Double screw rod compressor rotor molded line for oil injection |
| CN203867895U (en) * | 2014-05-20 | 2014-10-08 | 上海齐耀螺杆机械有限公司 | Tooth profile of rotor of dry twin-screw compressor |
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