CN103982425A - Tooth type of dry double-screw compressor rotor - Google Patents
Tooth type of dry double-screw compressor rotor Download PDFInfo
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- CN103982425A CN103982425A CN201410217700.6A CN201410217700A CN103982425A CN 103982425 A CN103982425 A CN 103982425A CN 201410217700 A CN201410217700 A CN 201410217700A CN 103982425 A CN103982425 A CN 103982425A
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Abstract
The invention discloses a tooth type of a dry double-screw compressor rotor, wherein a dry double-screw compressor comprises a female rotor and a male rotor, and is characterized in that all tooth types on the end surface of the female rotor are respectively formed by eight sections of quadratic curves which are smoothly connected end to end; all tooth types on the end surface of the male rotor are respectively formed by seven sections of curves which are smoothly connected end to end; each tooth curve on the end surface of the male rotor comprises an arc line and an arc envelope line; each tooth curve on the end surface of the female rotor comprises an arc line, an arc envelope line and a cycloid. After the technical scheme is adopted, the male rotor and the female rotor can be optimally meshed with each other in the working process, the tooth curve formed by every two adjacent sections has smooth transition at a connecting point, rotor contact lines are shorter, a leakage triangle is smaller, molded lines are in stream line forms, and the pneumatic resistance is low, so that the tooth type of the dry double-screw compressor rotor has excellent compressor thermodynamic performance, the working efficiency of the compressor is improved, the accuracy is improved in the processing process, and the service life of a cutter is prolonged.
Description
Technical field
The present invention relates to the rotor end-face flute profile of helical-lobe compressor, relate in particular to a kind of molded lines of rotor of dry type double-screw compressor.
Background technique
Helical-lobe compressor belongs to rotary type displacement equipment, can be under larger pressure versus flow scope, keep turning round under efficient state, molded lines of rotor of helical lobe compressor is the most critical factor that affects compressor performance, the area utilization factor of molded line affects the general structure of compressor, the line 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 very fast, its application constantly expands, particularly outstanding is, the output of helical-lobe compressor occupy the Japanese kobe steel of first place, the world, and the adiabatic efficiency of its new tooth has improved 10～20% than originally, and it is very large that the design of visible compressor drum improves compressor efficiency, therefore improving rotor design is compressor enterprise energy saving, increases economic efficiency reasonable approach is provided.But generally there are point, straight line etc. in the composition tooth curve of traditional molded line, be not easy to processing, easily cause tooth surface abrasion fast, and cutter leakage in straight line place is larger, and affects detection and the processing of rotor.
Summary of the invention
The object of the invention is: by the vector method of mathematics, be combined with algebraically up conversion method and develop a kind of flute profile of Novel dry rotor of helical lobe compressor, and draw out cutter, wherein flute profile comprises male rotor and the female rotor being meshed with it, their flute profile curve is by circular arc, cycloid and arc envelope line are formed by connecting, the compressor with this flute profile, owing to making male rotor and female rotor, realize in the course of the work optimal engagement, adjacent two sections form tooth curve in tie point place smooth transition, rotor Line of contact is shorter, leakage triangle is relatively little, it is streamlined that molded line becomes, aerodynamical resistance is little, there is good compressor heat mechanical property, thereby improve the working efficiency of compressor, and in course of working, improve precision, extend the life-span of cutter.
For achieving the above object: the technical solution adopted in the present invention is: a kind of flute profile of dry type double-screw compressor rotor, described dry type double-screw compressor comprises female rotor and male rotor, its feature is, each flute profile of the end face of female rotor is smoothly connected and forms from beginning to end by eight sections of quadratic curves, each flute profile of the end face of male rotor is smoothly connected and forms from beginning to end by seven sections of curves, wherein: the tooth curve of male rotor end face comprises circular arc line and arc envelope line; The tooth curve of female rotor end face comprises 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 following advantages:
Due to the employing of female rotor of the present invention larger tooth depth radius, flute profile area utilization factor has reached 56%, is very suitable for mesolow than the dry type helical-lobe compressor of large flow;
2. the Profile Design due to female rotor becomes streamlined, has reduced the disturbance resistance of air-flow, has reduced loss, has reduced noise, has improved the operational efficiency of rotor;
3. between the molded line flank of tooth, be smoothly connected, on molded line, without cusp, be convenient to adopt gear hobbing processing and detect, cutter life is increased greatly;
4. the front flank of tooth of this flute profile has adopted circular arc, and the rear flank of tooth has adopted circular arc and arc envelope line and cycloid, makes Line of contact relatively short, reveals like this triangle smaller, thereby makes sealing better.
Accompanying drawing explanation
Fig. 1 is a kind of example of female rotor of the present invention and male rotor schematic diagram when intermeshing.
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 tooth top radius of a circle of male rotor, and R2 is female rotor tooth top radius of a 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 distance 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 the radius of female rotor pin tooth circular arc A2B2 and male rotor pin tooth circular arc A1B1, equals the height of male rotor whole depth; 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 the center of circle of male rotor pin tooth circular arc A1B1 and female rotor pin tooth circular arc A2B2, and R3 is the radius of female rotor pin tooth circular arc A2B2 and male rotor pin tooth circular arc A1B1, equals the height of male rotor whole depth.
Embodiment
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 female rotor F of dry type double-screw compressor of the present invention and the rotor flute profile of male rotor M are 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 comprises female rotor F and male rotor M.Each flute profile of the end face of female rotor F is smoothly connected and forms from beginning to end by eight sections of quadratic curves, and each flute profile of the end face of male rotor M is smoothly connected and forms from beginning to end by seven sections of curves, wherein: the tooth curve of male rotor end face comprises circular arc line and arc envelope line; The tooth curve of female rotor end face comprises circular arc line, arc envelope line and cycloid.In the present embodiment: eight sections of curves of each flute profile of female rotor comprise that order is 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 comprise that order is 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 be take O3 as the center of circle, one section of pin tooth circular arc that R3 is radius;
Cycloid B2C2 is point gearing epicycloid, by the B1 point on male rotor pitch circle, at female rotor pitch circle, is formed outward as pure rolling;
Circular arc C 2D2 be take the O4 of female rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R4 of take; Radius R 4 is n1 times of female rotor Pitch radius, and n1 is greater than 0.1, is less than or equal to 0.4 positive number; Circular arc C 2D2 is smoothly connected at starting point C2 place and arc envelope line B2C2, in terminal D2 place and tangent connection of female rotor arc envelope line D2E2;
Arc envelope line D2E2 be by female rotor pitch circle when rolling on male rotor pitch circle, one section of arc envelope line of the formed track of male rotor C1D1 circular motion relatively;
Circular arc E2F2 be take the O5 of female rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R5 of take; Radius R 5 is n2 times of female rotor Pitch radius, and n2 is greater than 0.1, is less than or equal to 0.2 positive number; Circular arc E2F2 is smoothly connected at starting point E2 place and arc envelope line D2E2, in terminal F2 place and tangent connection of female rotor circular arc F2G2;
Circular arc F2G2 be take the O6 of female rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R6 of take; Radius R 6 is n3 times of female rotor Pitch radius, and n3 is greater than 1, is less than or equal to 2 positive number; Circular arc F2G2 is smoothly connected at starting point F2 place and circular arc E2F2, at the terminal of terminal G2 place and adjacent another tooth of this female rotor, is smoothly connected;
Arc envelope line A2H2 be by female rotor pitch circle when rolling on male rotor pitch circle, one section of arc envelope line of the formed track of male rotor A1H1 circular motion relatively;
Circular arc H2L2 be take the O7 of female rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R7 of take; Radius R 7 is n4 times of female rotor Pitch radius, and n4 is greater than 0.1, is less than or equal to 0.3 positive number; Circular arc H2L2 is smoothly connected at starting point H2 place and arc envelope line A2H2, at the terminal of terminal L2 place and adjacent another tooth of 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 be take O3 as the center of circle, one section of pin tooth circular arc that R3 is radius;
Arc envelope line B1C1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor C2D2 circular motion relatively;
Circular arc C 1D1 be take the O8 of male rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R8 of take; Radius R 8 is n5 times of male rotor Pitch radius, and n5 is greater than 0.3, is less than or equal to 0.5 positive number; Circular arc C 1D1 is smoothly connected at starting point C1 place and arc envelope line B1C1, in terminal D1 place and tangent connection of male rotor arc envelope line D1E1;
Arc envelope line D1E1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor E2F2 circular motion relatively;
Circular arc E1F1 be take the O9 of male rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R9 of take; Radius R 9 is n6 times of male rotor Pitch radius, and n6 is greater than 0, is less than or equal to 0.1 positive number; Circular arc E1F1 is smoothly connected at starting point E1 place and arc envelope line D1E1, at the terminal of terminal F1 place and adjacent another tooth of this male rotor, is smoothly connected;
Circular arc A1H1 be take the O10 of male rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R10 of take; Radius R 10 is n7 times of male rotor Pitch radius, and n7 is greater than 0.2, is less than or equal to 0.3 positive number; Circular arc A1H1 is smoothly connected at starting point A1 place and circular arc A1B1, at terminal H1 place and arc envelope line H1L1, is smoothly connected;
Arc envelope line H1L1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor H2L2 circular motion relatively.
In the specific implementation:
Described female rotor tooth curve A 2B2 circular arc is the common one section of circular arc determining of the radius of female rotor joint radius of a circle and pin tooth circular arc; Male rotor tooth curve A 1B1 circular arc is exactly and female rotor tooth curve A 2B2 circular arc one section of circular arc conjugation, on male rotor.
Described male rotor tooth curve B 1C1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor C2D2 circular motion relatively; Female rotor tooth curve cycloid B2C2 is point gearing epicycloid, by the B1 point on male rotor pitch circle, at female rotor pitch circle, is formed outward as pure rolling.
Described female rotor tooth curve C 2D2 circular arc be take the O4 of female rotor pitch circle inside as the center of circle, radius is one section of circular arc that R4 forms; Circular arc C 2D2 is smoothly connected in starting point and arc envelope line B2C2, at terminal, is connected with arc envelope line D2E2 is tangent; Male rotor tooth curve C 1D1 circular arc is that to take the O8 of male rotor pitch circle inside be the center of circle, and the R8 of take is one section of circular arc that radius forms, and circular arc C 1D1 is smoothly connected at starting point place and arc envelope line B1C1, tangent at destination county and male rotor arc envelope line D1E1.
Described male rotor tooth curve arc envelope line D1E1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor E2F2 circular motion relatively; Female rotor tooth curve arc envelope line D2E2 be by female rotor pitch circle when rolling on male rotor pitch circle, one section of arc envelope line of the formed track of male rotor C1D1 circular motion relatively.
Described female rotor tooth curve E2F2 circular arc be take the O5 of female rotor pitch circle inside as the center of circle, radius is one section of circular arc that R5 forms, circular arc E2F2 is smoothly connected at starting point place and arc envelope line D2E2, tangent at destination county and female rotor circular arc F2G2; Male rotor tooth curve E1F1 circular arc be take the O9 of male rotor pitch circle inside as the center of circle, the R9 of take is one section of circular arc that radius forms, circular arc E1F1 is smoothly connected at starting point place and circular arc D1E1, at the terminal of destination county and adjacent another tooth of this male rotor, is smoothly connected.
Described female rotor tooth curve F2G2 circular arc be take the O6 of female rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R6 of take, circular arc F2G2 is smoothly connected at starting point place and circular arc E2F2, at the terminal of destination county and adjacent another tooth of this female rotor, is smoothly connected.
Described male rotor tooth curve A 1H1 circular arc be take the O10 of male rotor pitch circle inside as the center of circle, the R10 of take is one section of circular arc that radius forms, circular arc A1H1 is smoothly connected at starting point place and circular arc A1B1, at destination county and arc envelope line H1L1, is smoothly connected; Female rotor tooth curve arc envelope line A2H2 be by female rotor pitch circle when rolling on male rotor pitch circle, one section of arc envelope line of the formed track of male rotor A1H1 circular motion relatively.
Described female rotor tooth curve H2L2 circular arc be take the O7 of female rotor pitch circle inside as the center of circle, one section of circular arc forming as radius of the R7 of take, circular arc H2L2 is smoothly connected at starting point place and arc envelope line A2H2, at the terminal of destination county and adjacent another tooth of this female rotor, is smoothly connected; Arc envelope line H1L1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor H2L2 circular motion relatively.
Like this, the end face tooth type of screw compressor rotor has just been done out completely.
Claims (6)
1. the flute profile of a dry type double-screw compressor rotor, described dry type double-screw compressor comprises female rotor and male rotor, it is characterized in that, each flute profile of the end face of described female rotor is smoothly connected and forms from beginning to end by eight sections of quadratic curves, each flute profile of the end face of described male rotor is smoothly connected and forms from beginning to end by seven sections of curves, wherein: the tooth curve of described male rotor end face comprises circular arc line and arc envelope line; The tooth curve of described female rotor end face comprises circular arc line, arc envelope line and cycloid.
2. the flute profile of a kind of dry type double-screw compressor rotor as claimed in claim 1, is characterized in that,
The tooth curve of each flute profile of female rotor comprises that order is 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 comprises that order is 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.
3. the flute profile of a kind of dry type double-screw compressor rotor as claimed in claim 2, is characterized in that, in the tooth curve of each flute profile of described female rotor:
Circular arc A2B2 be take O3 as the center of circle, one section of pin tooth circular arc that R3 is radius;
Cycloid B2C2 is point gearing epicycloid, by the B1 point on male rotor pitch circle, at female rotor pitch circle, is formed outward as pure rolling;
Circular arc C 2D2 be take the O4 of female rotor pitch circle inside as the center of circle, radius is one section of circular arc that n1 times of female rotor Pitch radius forms; Circular arc C 2D2 is smoothly connected at starting point C2 place and arc envelope line B2C2, and in terminal D2 place and tangent connection of female rotor arc envelope line D2E2, n1 is greater than 0.1, is less than or equal to 0.4 positive number;
Arc envelope line D2E2 be by female rotor pitch circle when rolling on male rotor pitch circle, one section of arc envelope line of the formed track of male rotor C1D1 circular motion relatively;
Circular arc E2F2 be take the O5 of female rotor pitch circle inside as the center of circle, radius is one section of circular arc that n2 times of female rotor Pitch radius forms; Circular arc E2F2 is smoothly connected at starting point E2 place and arc envelope line D2E2, and in terminal F2 place and tangent connection of female rotor circular arc F2G2, n2 is greater than 0.1, is less than or equal to 0.2 positive number;
Circular arc F2G2 be take the O6 of female rotor pitch circle inside as the center of circle, radius is one section of circular arc that n3 times of female rotor Pitch radius forms; Circular arc F2G2 is smoothly connected at starting point F2 place and circular arc E2F2, at the terminal of terminal G2 place and adjacent another tooth of this female rotor, is smoothly connected, and n3 is greater than 1, is less than or equal to 2 positive number;
Arc envelope line A2H2 be by female rotor pitch circle when rolling on male rotor pitch circle, one section of arc envelope line of the formed track of male rotor A1H1 circular motion relatively;
Circular arc H2L2 be take the O7 of female rotor pitch circle inside as the center of circle, radius is one section of circular arc that n4 times of female rotor Pitch radius forms, circular arc H2L2 is smoothly connected at starting point H2 place and arc envelope line A2H2, terminal at terminal L2 place and adjacent another tooth of this female rotor is smoothly connected, and n4 is greater than 0.1, is less than or equal to 0.3 positive number.
4. the flute profile of a kind of dry type double-screw compressor rotor as claimed in claim 2, is characterized in that, in the tooth curve of each flute profile of described male rotor:
Circular arc A1B1 be take O3 as the center of circle, one section of pin tooth circular arc that R3 is radius;
Arc envelope line B1C1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor C2D2 circular motion relatively;
Circular arc C 1D1 be take the O8 of male rotor pitch circle inside as the center of circle, radius is one section of circular arc that n5 times of male rotor Pitch radius forms; Circular arc C 1D1 is smoothly connected at starting point C1 place and arc envelope line B1C1, and in terminal D1 place and tangent connection of male rotor arc envelope line D1E1, n5 is greater than 0.3, is less than or equal to 0.5 positive number;
Arc envelope line D1E1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor E2F2 circular motion relatively;
Circular arc E1F1 be take the O9 of male rotor pitch circle inside as the center of circle, radius is one section of circular arc that n6 times of male rotor Pitch radius forms; Circular arc E1F1 is smoothly connected at starting point E1 place and arc envelope line D1E1, at the terminal of terminal F1 place and adjacent another tooth of this male rotor, is smoothly connected, and n6 is greater than 0, is less than or equal to 0.1 positive number;
Circular arc A1H1 be take the O10 of male rotor pitch circle inside as the center of circle, radius is one section of circular arc that n7 times of male rotor Pitch radius forms; Circular arc A1H1 is smoothly connected at starting point A1 place and circular arc A1B1, at terminal H1 place and arc envelope line H1L1, is smoothly connected, and n7 is greater than 0.2, is less than or equal to 0.3 positive number;
Arc envelope line H1L1 be by male rotor pitch circle when rolling on female rotor pitch circle, one section of arc envelope line of the formed track of female rotor H2L2 circular motion relatively.
5. the flute profile of a kind of dry type double-screw compressor rotor as claimed in claim 1, is characterized 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 a kind of dry type double-screw compressor rotor as claimed in claim 5, is characterized in that, the gear ratio of described male rotor and female rotor is 4:6.
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| Application Number | Priority Date | Filing Date | Title |
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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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| CN103982425B CN103982425B (en) | 2016-06-08 |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109026163A (en) * | 2018-09-18 | 2018-12-18 | 上海齐耀膨胀机有限公司 | The flute profile of high pressure ratio High Pressure Difference twin-screw expander rotor |
| CN113217380A (en) * | 2021-05-24 | 2021-08-06 | 中国船舶重工集团公司第七一一研究所 | Double-screw compressor rotor designed based on intelligent algorithm |
| CN114320912A (en) * | 2021-12-23 | 2022-04-12 | 湖南慧风流体科技有限公司 | Double-screw bilateral asymmetric rotor profile composed of nine-section tooth curves |
| 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 |
| CN118030520A (en) * | 2024-03-04 | 2024-05-14 | 中国科学院理化技术研究所 | Single-stage high-pressure-ratio streamline helium screw rotor molded line |
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| 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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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109026163A (en) * | 2018-09-18 | 2018-12-18 | 上海齐耀膨胀机有限公司 | The flute profile of high pressure ratio High Pressure Difference twin-screw expander rotor |
| 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 |
| CN114320912A (en) * | 2021-12-23 | 2022-04-12 | 湖南慧风流体科技有限公司 | Double-screw bilateral asymmetric rotor profile composed of nine-section tooth curves |
| 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 |
| CN118030520A (en) * | 2024-03-04 | 2024-05-14 | 中国科学院理化技术研究所 | Single-stage high-pressure-ratio streamline helium screw rotor molded line |
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| CN103982425B (en) | 2016-06-08 |
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