CN205297915U - Flute profile of two helical -lobe compressor rotors - Google Patents

Flute profile of two helical -lobe compressor rotors Download PDF

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Publication number
CN205297915U
CN205297915U CN201521081670.7U CN201521081670U CN205297915U CN 205297915 U CN205297915 U CN 205297915U CN 201521081670 U CN201521081670 U CN 201521081670U CN 205297915 U CN205297915 U CN 205297915U
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circular arc
rotor
arc
envelope line
radius
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杨剑
林艳斐
卢笋
王莹
张明珠
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SHANGHAI QIYAO SCREW MACHINERY CO Ltd
Shanghai Marine Diesel Engine Research Institute
711th Research Institute of CSIC
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SHANGHAI QIYAO SCREW MACHINERY CO Ltd
711th Research Institute of CSIC
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Abstract

The utility model discloses a flute profile of two helical -lobe compressor rotors, two helical -lobe compressor include female rotor and male rotor, and its characteristics lie in that each flute profile of the terminal surface of female rotor smoothly is formed by connecting eight sections quadratic curve head and the tail nine sections smooth being formed by connecting of quadratic curve head and the tail, each flute profile of the terminal surface of male rotor, wherein: the tooth curve of male rotor terminal surface includes circular arc line and arc envelope line, the tooth curve of female rotor terminal surface includes circular arc line, arc envelope line and cycloid. After adopting above -mentioned technical scheme, realize best meshing owing to enabling the male rotor in the course of the work with the female rotor, constitute the tooth curves for adjacent two sections and locate smooth transition at the tie point that utilization coefficient is bigger for the rotor area, the contact wire is shorter, and it is less relatively to leak triangle -shaped, and the molded lines becomes streamlined, has compressor thermodynamic property well to improve helical -lobe compressor's work efficiency.

Description

The flute profile of double-screw compressor rotor
Technical field
This utility model relates to the rotor end-face flute profile of helical-lobe compressor, particularly relates to the molded lines of rotor of a kind of double-screw compressor.
Background technology
Helical-lobe compressor has the advantages such as simple in construction, easy to operate, few easy workout part, member replacing convenient, operational security is reliable, therefore obtains in industrial department and is increasingly widely applied. The development of helical-lobe compressor depends greatly on design and the processing of screw rotor molded line. Molded lines of rotor is by the path of contact sealing to reach between rotor, therefore reduces gas leakage triangle area, shortens contact line length, reduces leakage to greatest extent and become the key improving compressor efficiency. In addition, improve area utilization factor, improve rotor and the intensity of tooth, rigidity, improve the power performance of rotor and improve gas flowing rotary state between teeth groove etc., the performance of helical-lobe compressor is also had a certain impact, and everything is invariably closely bound up with the flute profile of compressor drum. Along with people are more and more higher to the requirement of compressor operating efficiency, the flute profile of rotor is carried out the demand that innovation improves also further urgent. First it is to the requirement sealed, namely requires that molded line can make compressor have air-tightness axially and transversely. Particularly, except requiring that rotor contact line is continuously, also requiring that leakage triangle area is as far as possible little, contact wire is as far as possible short. And actually this is the factor mutually restricted for a pair, it is impossible to reach the index being satisfied with most simultaneously. When designing molded lines of rotor, it is crucial that to match the relation of both, next to that require that molded lines of rotor has bigger area utilization factor, so not only the volume of compressor can reduce, and the leakage loss of unit capacity also to be lacked, the work efficiency of compressor can be made relatively to improve. It addition, molded line preferably streaming, to reduce gas flow loss, to be also easy to processing.
Summary of the invention
The purpose of this utility model is: is combined with graphic-arts technique with the algebraic approach of mathematics and develops a kind of new rotor of helical lobe compressor flute profile, wherein flute profile includes male rotor and meshed female rotor, their tooth curve is by point, cycloid, circular arc 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 area usage factor is relatively larger, contact wire is shorter, leakage triangle is relatively small, molded line becomes streamlined, the compressor heat mechanical property having had, thus improving the work efficiency of helical-lobe compressor, and in the course of processing, improve precision, extend the life-span of cutter.
For solving above-mentioned technical problem, technical solution adopted in the utility model is:
The flute profile of double-screw compressor rotor, described 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 nine sections of conic section head and the tail and forms, each flute profile of the end face of male rotor is smoothly connected by eight sections of conic section 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 female rotor end face includes circular arc line, arc envelope line and cycloid.
The algebraic approach of this utility model employing mathematics is combined with geometric projection 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. this utility model is by adopting circular arc and envelope as easement curve between tooth root circular arc and tooth top circular arc, tooth root, tooth top circular arc and easement curve is made to form smooth connection, leaking area and stagnant area can be avoided the formation of, forming strict seal, the change of the end face being consequently formed promotes joint with improved dynamic behaviour. Easement curve makes tooth root and the smooth connection of flank profil position of rotor simultaneously, effectively reduces manufacturing cost;
2. the profile of tooth of male rotor and female rotor be with pin tooth circular arc, circular arc and arc envelope line, point and cycloid and be basic component units to round as a ball arc conic section bilateral unsymmetrical tooth profile, helical lobe compressor host efficiency 8% can be improved, complete machine group input specific power is up to state standards one-level efficiency, is particularly suited for the helical-lobe compressor of the big flow of low-pressure ratio;
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. in this utility model, rear end point forms with cycloid with triangle of stopping a leak, and front end adopts circular arc and arc envelope line to form to shorten contact line length, plays reasonable linear sealing effect. Not being direct contact due to molded lines of rotor in compressor, the length of contact wire can be relatively larger on the impact of compressor tolerance, and the length of this utility model contact wire is relatively short, decreases the leakage of compressor largely, and relative efficiency is higher.
Accompanying drawing explanation
Fig. 1 is a kind of example of this utility model female rotor and the male rotor schematic diagram when engaging each other.
Fig. 2 is the flute profile line schematic diagram of this utility model female rotor.
Fig. 3 is the flute profile line schematic diagram of this utility model male rotor.
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; O5 is node; Mj is the pitch circle of male rotor, and R1j is the pitch radius of male rotor; Fj is the pitch circle of female rotor, and R2j is the pitch radius of female rotor; A is the centre-to-centre spacing of two rotors, A=R1j+R2j; O3 is the center of circle of female rotor circular arc B2C2, and R3 is the radius of female rotor circular arc B2C2; O4 is the center of circle of female rotor circular arc D2E2, and R4 is the radius of female rotor circular arc D2E2; O5 is female rotor pin tooth circular arc F2G2 and the center of circle of male rotor pin tooth circular arc F1G1, and R5 is female rotor pin tooth circular arc F2G2 and the radius of male rotor pin tooth circular arc F1G1; O6 is the center of circle of female rotor pin tooth circular arc H2I2, and R6 is the radius of female rotor circular arc H2I2; O7 is the center of circle of male rotor circular arc A1B1, and R7 is the radius of male rotor circular arc A1B1; O8 is the center of circle of female rotor circular arc C 1D1, and R8 is the radius of female rotor circular arc C 1D1; O9 is the center of circle of male rotor circular arc G1H1, and R9 is the radius of male rotor circular arc G1H1;O10 is the center of circle of male rotor circular arc I1J1, and R10 is the radius of male rotor circular arc I1J1.
Detailed description of the invention
Below in conjunction with the drawings and specific embodiments, the flute profile of this utility model double-screw compressor rotor is described in detail.
Refer to Fig. 1 to Fig. 3. The rotor flute profile of the female rotor F and male rotor M of double-screw compressor of the present utility model 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 3:5.
The flute profile of the dry type double-screw compressor rotor according to this utility model one embodiment, described 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 nine 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 eight sections of conic section 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: the tooth curve of each flute profile of female rotor includes what order was smoothly connected: arc envelope line A2B2, circular arc B2C2, arc envelope line C2D2, circular arc D2E2, cycloid E2F2, pin tooth circular arc F2G2, arc envelope line G2H2, circular arc H2I2 and arc envelope line I2J2; The tooth curve of each flute profile of male rotor includes what order was smoothly connected: circular arc A1B1, arc envelope line B1C1, circular arc C 1D1, arc envelope line D1E1, pin tooth circular arc F1G1, circular arc G1H1, arc envelope line H1I1 and circular arc I1J1, wherein, the terminal E1 of arc envelope line D1E1 overlaps with the starting point of pin tooth circular arc F1G1.
Please refer to Fig. 2. In the tooth curve of each flute profile of female rotor:
Arc envelope line A2B2 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 circular arc A1B1 motion is formed;
Circular arc B2C2 be with the O3 within female rotor pitch circle be the center of circle, with the R3 one section of circular arc formed for radius, radius R3 is n1 times of female rotor pitch radius, n1 is the positive number more than 0.1, less than or equal to 0.3, circular arc B2C2 is smoothly connected at starting point B2 place and arc envelope line A2B2, tangent with female rotor arc envelope line C2D2 at terminal C2 place is connected;
Arc envelope line C2D2 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 circular arc C 1D1 motion is formed;
Circular arc D2E2 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 n2 times of female rotor pitch radius, n2 is the positive number more than 0.2, less than or equal to 0.3, circular arc D2E2 is smoothly connected at starting point D2 place and circular arc C 2D2, tangent with female rotor cycloid E2F2 at terminal E2 place is connected;
Cycloid E2F2 is point gearing epicycloid, the F1 point on male rotor pitch circle make pure rolling outside female rotor pitch circle and formed;
Pin tooth circular arc F2G2 be with node O5 be the center of circle, R5 be radius one section of pin tooth circular arc;
Arc envelope line G2H2 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 circular arc G1H1 motion is formed;
Circular arc H2I2 be with the O6 within female rotor pitch circle be the center of circle, R6 be radius one section of circular arc, radius R6 is n3 times of female rotor pitch radius, n3 is the positive number more than 0.1, less than or equal to 0.3, circular arc H2I2 is smoothly connected at starting point H2 place and circular arc G2H2, tangent with female rotor arc envelope line I2J2 at terminal I2 place is connected;
Arc envelope line I2J2 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 circular arc I1J1 motion is formed.
Please refer to Fig. 3. In the tooth curve of each flute profile of male rotor:
Circular arc A1B1 be with the O7 outside male rotor pitch circle be the center of circle, R7 be radius one section of circular arc, radius R7 is n4 times of male rotor pitch radius, n4 is the positive number more than 0.1, less than or equal to 0.2, circular arc A1B1 is smoothly connected with arc envelope line B1C1 at terminal B1 place, and at starting point A1 place, the terminal of another tooth adjacent with this male rotor is smoothly connected;
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 circular arc B2C2 motion is formed;
Circular arc C 1D1 be with the O8 within male rotor pitch circle be the center of circle, R8 be radius one section of circular arc, radius R8 is n5 times of male rotor pitch radius, 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 circular arc D2E2 motion is formed;
Pin tooth circular arc F1G1 be with node O5 be the center of circle, R5 be radius one section of pin tooth circular arc;
Circular arc G1H1 be with the O9 within male rotor pitch circle be the center of circle, R9 be radius one section of circular arc, radius R9 is n6 times of male rotor pitch radius, n6 is the positive number more than 0.3, less than or equal to 0.5, circular arc G1H1 is smoothly connected at starting point G1 place and circular arc F1G1, tangent with male rotor arc envelope line H1I1 at terminal H1 place is connected;
Arc envelope line H1I1 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 circular arc H2I2 motion is formed;
Circular arc I1J1 be with the O10 outside male rotor pitch circle be the center of circle, R10 is for one section of circular arc of radius, radius R10 is n7 times of male rotor pitch radius, n7 is the positive number more than 0.1, less than or equal to 0.5, circular arc I1J1 is smoothly connected with circular arc H1I1 at starting point I1 place, and the starting point at terminal J1 place another tooth adjacent with this male rotor is smoothly connected.
In the specific implementation:
Described female rotor tooth curve A2B2 arc envelope line 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 A1B1 circular motion is formed; Male rotor tooth curve A1B1 circular arc be with the O7 outside male rotor pitch circle be the center of circle, R7 be radius one section of circular arc, radius R7 is n4 times of female rotor pitch radius, n4 is the positive number more than 0.1, less than or equal to 0.2, circular arc A1B1 is smoothly connected with arc envelope line B1C1 at terminal B1 place, and at starting point A1 place, the terminal of another tooth adjacent with this male rotor is smoothly connected.
Described female rotor tooth curve B2C2 circular arc be with the O3 within female rotor pitch circle be the center of circle, with the R3 one section of circular arc formed for radius, radius R3 is n1 times of female rotor pitch radius, n1 is the positive number more than 0.1, less than or equal to 0.3, circular arc B2C2 is smoothly connected at starting point B2 place and arc envelope line A2B2, tangent with female rotor arc envelope line C2D2 at terminal C2 place is connected; 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 B2C2 circular motion is formed.
Described female rotor tooth curve C2D2 arc envelope line 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;Male rotor tooth curve C1D1 circular arc be with the O8 within male rotor pitch circle be the center of circle, R8 be radius one section of circular arc, radius R8 is n5 times of male rotor pitch radius, 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.
Described female rotor tooth curve D2E2 circular arc 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 n2 times of female rotor pitch radius, n2 is the positive number more than 0.2, less than or equal to 0.3, circular arc D2E2 is smoothly connected at D2 place starting point and circular arc C 2D2, tangent with female rotor cycloid E2F2 at terminal E2 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 D2E2 circular motion is formed.
Described female rotor tooth curve cycloid E2F2 is point gearing epicycloid, the F1 on male rotor pitch circle make pure rolling outside female rotor pitch circle and formed; The male rotor tooth E1F1 cycloid corresponding with cycloid E2F2 is exactly a some F1.
Described female rotor tooth curve F2G2 circular arc is with node O5 for the center of circle, and R5 is one section of pin tooth circular arc of radius; Male rotor tooth curve F1G1 circular arc be with node O5 be the center of circle, R5 be radius one section of pin tooth circular arc.
Described female rotor tooth curve G2H2 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 G1H1 circular motion is formed; Male rotor tooth curve G1H1 circular arc be be the center of circle at the O9 within male rotor pitch circle, R9 be radius one section of circular arc, radius R9 is n6 times of male rotor pitch radius, n6 is the positive number more than 0.3, less than or equal to 0.5, circular arc G1H1 is smoothly connected at starting point G1 place and circular arc F1G1, tangent with male rotor arc envelope line H1I1 at terminal H1 place is connected.
Described female rotor tooth curve H2I2 circular arc be with the O6 within female rotor pitch circle be the center of circle, R6 be radius one section of circular arc, radius R6 is n3 times of female rotor pitch radius, n3 is the positive number more than 0.1, less than or equal to 0.3, circular arc H2I2 is smoothly connected with circular arc G2H2 at starting point H2 place, tangent with female rotor arc envelope line I2J2 at terminal I2 place; Arc envelope line H1I1 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 H2I2 circular motion is formed.
Described female rotor tooth curve I2J2 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 I1J1 circular motion is formed; Male rotor tooth curve I1J1 circular arc be with the O10 outside male rotor pitch circle be the center of circle, R10 is for one section of circular arc of radius, radius is n7 times of male rotor pitch radius, n7 is the positive number more than 0.1, less than or equal to 0.5, circular arc I1J1 is smoothly connected with circular arc H1I1 at starting point I1 place, and the starting point at terminal J1 place another tooth adjacent with this male rotor is smoothly connected.
So, the end face tooth type of screw compressor rotor just is made out completely.

Claims (6)

1. the flute profile of double-screw compressor rotor, described 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 nine 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 eight sections of conic section 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.
2. the flute profile of double-screw compressor rotor according to claim 1, it is characterized in that, the tooth curve of each flute profile of female rotor includes what order was smoothly connected: arc envelope line A2B2, circular arc B2C2, arc envelope line C2D2, circular arc D2E2, cycloid E2F2, pin tooth circular arc F2G2, arc envelope line G2H2, circular arc H2I2 and arc envelope line I2J2;
The tooth curve of each flute profile of male rotor includes what order was smoothly connected: circular arc A1B1, arc envelope line B1C1, circular arc C 1D1, arc envelope line D1E1, pin tooth circular arc F1G1, circular arc G1H1, arc envelope line H1I1 and circular arc I1J1, wherein, the terminal E1 of arc envelope line D1E1 overlaps with the starting point of pin tooth circular arc F1G1.
3. the flute profile of double-screw compressor rotor according to claim 2, it is characterised in that in the tooth curve of each flute profile of described female rotor:
Arc envelope line A2B2 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 circular arc A1B1 motion is formed;
Circular arc B2C2 be with the O3 within female rotor pitch circle be the center of circle, with the R3 one section of circular arc formed for radius, radius R3 is n1 times of female rotor pitch radius, n1 is the positive number more than 0.1, less than or equal to 0.3, circular arc B2C2 is smoothly connected at starting point B2 place and arc envelope line A2B2, tangent with female rotor arc envelope line C2D2 at terminal C2 place is connected;
Arc envelope line C2D2 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 circular arc C 1D1 motion is formed;
Circular arc D2E2 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 n2 times of female rotor pitch radius, n2 is the positive number more than 0.2, less than or equal to 0.3, circular arc D2E2 is smoothly connected at starting point D2 place and circular arc C 2D2, tangent with female rotor cycloid E2F2 at terminal E2 place is connected;
Cycloid E2F2 is point gearing epicycloid, the F1 point on male rotor pitch circle make pure rolling outside female rotor pitch circle and formed;
Pin tooth circular arc F2G2 be with node O5 be the center of circle, R5 be radius one section of pin tooth circular arc;
Arc envelope line G2H2 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 circular arc G1H1 motion is formed;
Circular arc H2I2 be with the O6 within female rotor pitch circle be the center of circle, R6 be radius one section of circular arc, radius R6 is n3 times of female rotor pitch radius, n3 is the positive number more than 0.1, less than or equal to 0.3, circular arc H2I2 is smoothly connected at starting point H2 place and circular arc G2H2, tangent with female rotor arc envelope line I2J2 at terminal I2 place is connected;
Arc envelope line I2J2 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 circular arc I1J1 motion is formed.
4. the flute profile of the double-screw compressor rotor according to Claims 2 or 3, it is characterised in that in the tooth curve of each flute profile of described male rotor:
Circular arc A1B1 be with the O7 outside male rotor pitch circle be the center of circle, R7 be radius one section of circular arc, radius R7 is n4 times of male rotor pitch radius, n4 is the positive number more than 0.1, less than or equal to 0.2, circular arc A1B1 is smoothly connected with arc envelope line B1C1 at terminal B1 place, and at starting point A1 place, the terminal of another tooth adjacent with this male rotor is smoothly connected;
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 circular arc B2C2 motion is formed;
Circular arc C 1D1 be with the O8 within male rotor pitch circle be the center of circle, R8 be radius one section of circular arc, radius R8 is n5 times of male rotor pitch radius, 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 circular arc D2E2 motion is formed;
Pin tooth circular arc F1G1 be with node O5 be the center of circle, R5 be radius one section of pin tooth circular arc;
Circular arc G1H1 be with the O9 within male rotor pitch circle be the center of circle, R9 be radius one section of circular arc, radius R9 is n6 times of male rotor pitch radius, n6 is the positive number more than 0.3, less than or equal to 0.5, circular arc G1H1 is smoothly connected at starting point G1 place and circular arc F1G1, tangent with male rotor arc envelope line H1I1 at terminal H1 place is connected;
Arc envelope line H1I1 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 circular arc H2I2 motion is formed;
Circular arc I1J1 be with the O10 outside male rotor pitch circle be the center of circle, R10 is for one section of circular arc of radius, radius R10 is n7 times of male rotor pitch radius, n7 is the positive number more than 0.1, less than or equal to 0.5, circular arc I1J1 is smoothly connected with circular arc H1I1 at starting point I1 place, and the starting point at terminal J1 place another tooth adjacent with this male rotor is smoothly connected.
5. the flute profile of double-screw compressor rotor according to 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.
6. the flute profile of double-screw compressor rotor according to claim 1, it is characterised in that the gear ratio of described male rotor and female rotor is 3:5.
CN201521081670.7U 2015-12-22 2015-12-22 Flute profile of two helical -lobe compressor rotors Active CN205297915U (en)

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Application Number Priority Date Filing Date Title
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105443380A (en) * 2015-12-22 2016-03-30 上海齐耀螺杆机械有限公司 Tooth form of rotor of twin-screw compressor
CN110080980A (en) * 2019-03-28 2019-08-02 中国石化工程建设有限公司 A kind of flute profile of dual-screw-stem machine rotor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105443380A (en) * 2015-12-22 2016-03-30 上海齐耀螺杆机械有限公司 Tooth form of rotor of twin-screw compressor
CN110080980A (en) * 2019-03-28 2019-08-02 中国石化工程建设有限公司 A kind of flute profile of dual-screw-stem machine rotor
CN110080980B (en) * 2019-03-28 2021-03-09 中国石化工程建设有限公司 Tooth profile of double-screw machine rotor

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