CN114876796A - Novel double-screw compressor rotor profile - Google Patents
Novel double-screw compressor rotor profile Download PDFInfo
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- CN114876796A CN114876796A CN202210667566.4A CN202210667566A CN114876796A CN 114876796 A CN114876796 A CN 114876796A CN 202210667566 A CN202210667566 A CN 202210667566A CN 114876796 A CN114876796 A CN 114876796A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/20—Rotors
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Rotary-Type Compressors (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The rotor profile of the double-screw compressor comprises a male rotor profile and a female rotor profile, wherein the tooth profiles of the male rotor and the female rotor are bilateral asymmetric tooth profiles which take circular arcs and circular arc envelope lines as basic composition units. The male rotor profile and the female rotor profile are obtained by analyzing a meshing envelope principle, the arcs and the arc envelope lines are all used as bilateral asymmetric tooth profiles of basic composition units, adjacent curves are connected in a smooth and tangent mode, contact lines are continuous, and meshing lines are completely closed. The rotor is streamline, the sharp point in the tooth form is thoroughly eliminated, the length of the contact line is moderate, and the leakage triangle area on the high-pressure side is small. During production, a driving belt (with the length of 2-3mm) is set near the pitch circle of the long edge of the male rotor and the female rotor, and reasonable gaps are left in the rest positions. The male and female rotors roll only without relative sliding, so that the abrasion can be reduced, the transmission is stable, and the noise and vibration are reduced. The female rotor has thick teeth and higher strength. The rotor area utilization coefficient is large.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a rotor structure of a double-screw compressor, and particularly relates to a novel rotor profile of the double-screw compressor.
Background
The rotor of the double-screw compressor is a core component of the screw compressor, and the molded lines of the rotor fundamentally determine the overall performance of the screw compressor. The female and male rotor profiles are composed of several different primary or secondary mathematical curves, such as circular arcs and circular arc envelope curves, point (straight line) cycloid curves, ellipse and ellipse envelope curves, parabola curves and parabola envelope curves, etc., the corresponding curve of each segment between the female and male rotors is obtained by analyzing according to the meshing envelope principle, and different curves are in tangential connection and are in smooth transition.
An excellent rotor profile requires a smooth tooth profile (small flow loss), a continuous contact line (good sealing effect) and is as short as possible, a leakage triangle (internal leakage reduction), a closed volume is small, grinding processability is good (easy to process), and the current-generation profile design abandons an early point (straight line) cycloid (sensitive to meshing performance and processability) and completely adopts a smooth mathematical curve (such as an arc, an ellipse, a parabola and the like), so that the sealing mode of the sealing side of the rotor is converted from the traditional point (line) -arc sealing into an arc-arc sealing strip, the internal leakage is reduced, and the volumetric efficiency is improved. However, the traditional female rotor has thinner teeth and weaker tooth strength, and is not easy to process.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides a novel rotor molded line of a double-screw compressor, and aiming at the problems that the teeth of the female rotor of the prior double-screw compressor are thin, weak in strength and difficult to process, the rotor molded line of the double-screw compressor is designed, and the rotor molded line of the double-screw compressor is thick in teeth, large in strength, easy to process, stable in transmission and low in vibration and noise.
In order to achieve the purpose, the invention is realized by the following technical scheme:
the rotor profile of the double-screw compressor comprises a male rotor profile and a female rotor profile, wherein the tooth profiles of the male rotor and the female rotor are bilateral asymmetric tooth profiles which take circular arcs and circular arc envelope lines as basic composition units.
Preferably, the male rotor is composed of six quadratic curve units, namely a male rotor first arc HI, a male rotor second arc IJ, a male rotor third arc JK, a male rotor fourth arc KL, a male rotor arc envelope LM and a male rotor fifth arc MN;
the female rotor is composed of six quadratic curve units, namely a female rotor first arc envelope line AB, a female rotor second arc envelope line BC, a female rotor third arc envelope line CD, a female rotor fourth arc envelope line DE, a female rotor first arc EF and a female rotor addendum arc FG.
Preferably, O1 is used as the center of the male rotor, O2 is used as the center of the female rotor, and A is the center distance between the male rotor and the female rotor; rd1, Rt1 and Rg1 respectively and sequentially represent a addendum circle radius, a pitch circle radius and a dedendum circle radius of the male rotor, Rd2, Rt2 and Rg2 respectively and sequentially represent a addendum circle radius, a pitch circle radius and a dedendum circle radius of the female rotor, wherein Rd1 is 0.65-0.71A, Rg1 is 0.39-0.5A, Rg2 is A-Rg1, and Rd2 is A-Rd 1;
Preferably, the center O (HI) of the first arc HI of the male rotor falls on an extension line which takes O1 as an origin and has an included angle α 1 with the joint line O1O2, and the first arc HI of the male rotor is tangent to the root circle Rg1 of the male rotor at the point H and tangent to the second arc IJ of the male rotor at the point J; arc radius r (hi) 0.07-0.1A;
the male rotor second arc IJ is tangent to the male rotor first arc HI at the point I and tangent to the male rotor third arc JK at the point J; the arc radius r (hi) of the second arc IJ of the male rotor is 0.30-0.38A;
the center of the third arc JK of the male rotor is on a straight line O1O2 and is positioned outside a pitch circle of the male rotor, and the arc radius R (JK) of the third arc JK of the male rotor is Rd1-Rt1-Kappa, wherein Kappa is the distance from the center of the arc JK to the pitch circle of the male rotor and is 0.001-0.012A;
the center of the fourth circular arc KL of the male rotor is on a straight line O1O2, the circular arc radius R (JK) of the fourth circular arc KL of the male rotor is 0.03-0.05A, and the radius R (JK) is tangent to a point k together with the third circular arc JK of the male rotor;
the male rotor circular arc envelope line LM is generated by a female rotor first circular arc EF defined on the female rotor and is tangent to a point L with a male rotor fourth circular arc KL;
the circle center of the fifth circular arc MN of the male rotor is O1, namely the tooth root circular arc of the male rotor is tangent to the envelope LM of the circular arc LM of the male rotor at the point M.
Preferably, the first arc envelope AB is a conjugate curve of the first arc HI of the male rotor; the envelope CD of the third arc of the female rotor is a conjugate curve of the third arc JK of the male rotor; the fourth arc envelope DE of the female rotor is a conjugate curve of a fourth arc KL of the male rotor;
the center of the first circular arc EF of the female rotor is on a straight line O2F and is positioned within a pitch circle of the female rotor, the radius R (EF) of the first circular arc EF of the female rotor is 0.010-0.035A, the radius Rd2 is R (EF) + Rt2-lambda, lambda is the distance from the center of the first circular arc EF of the female rotor to the pitch circle of the female rotor, and lambda takes a positive number and is tangent to a fourth circular arc envelope DE of the female rotor at a point E; tangent to the F point with the addendum arc FG of the female rotor;
and the addendum arc FG of the female rotor is a conjugate curve of a fifth arc MN of the male rotor.
Preferably, the gear ratio of the male rotor to the female rotor is 4-6: 5 to 8.
The invention provides a novel double-screw compressor rotor profile. The method has the following beneficial effects: the male rotor molded line and the female rotor molded line are obtained by analyzing a meshing envelope principle, are all bilateral asymmetric tooth forms taking circular arcs and circular arc envelope lines as basic composition units, are connected between adjacent curves in a smooth and tangent mode, are continuous in contact line, and are completely closed in meshing line. The rotor is streamline, the sharp point in the tooth form is thoroughly eliminated, the length of the contact line is moderate, and the leakage triangle area on the high-pressure side is small. During production and processing, a driving belt is set near the pitch circle of the long edge of the male rotor and the long edge of the female rotor, and reasonable gaps are left in the rest positions. The male and female rotors roll only without relative sliding, so that the abrasion can be reduced, the transmission is stable, and the noise and vibration are reduced. The female rotor has thick teeth and higher strength. The rotor area utilization coefficient is large.
Drawings
In order to more clearly illustrate the present invention or the prior art solutions, the drawings that are needed in the description of the prior art will be briefly described below.
FIG. 1 is a schematic structural view of a rotor profile meshing state of the twin-screw compressor according to the present invention;
FIG. 2 is a meshing line diagram of the present invention;
figure 3 is a triangular plot of leakage from the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings.
As shown in figures 1 to 3, the rotor profile of the novel double-screw compressor comprises a male rotor profile 1 and a female rotor profile 2, wherein the gear ratio of the male rotor to the female rotor is 4-6: 5-8; 4 can be selected according to the working conditions of low, medium and high exhaust pressures: 5. 4: 6. 5: 6. 5: 7. 6: 7. 6: 8, and the like in different combinations.
The tooth profiles of the male rotor and the female rotor are all bilateral asymmetric tooth profiles taking arcs and arc envelope lines as basic constituent units.
The male rotor consists of six quadratic curve units, namely a male rotor first arc HI, a male rotor second arc IJ, a male rotor third arc JK, a male rotor fourth arc KL, a male rotor arc envelope line LM and a male rotor fifth arc MN;
the female rotor is composed of six quadratic curve units, namely a female rotor first arc envelope line AB, a female rotor second arc envelope line BC, a female rotor third arc envelope line CD, a female rotor fourth arc envelope line DE, a female rotor first arc EF and a female rotor addendum arc FG.
Taking O1 as the center of the male rotor, O2 as the center of the female rotor and A as the center distance of the male rotor and the female rotor; rd1, Rt1 and Rg1 are respectively a addendum circle radius, a pitch circle radius and a dedendum circle radius of the male rotor in sequence, and Rd2, Rt2 and Rg2 are respectively a addendum circle radius, a pitch circle radius and a dedendum circle radius of the female rotor in sequence, wherein Rd1 is 0.65-0.71A, Rg1 is 0.39-0.5A, Rg2 is A-Rg1, and Rd2 is A-Rd 1;
The center O (HI) of the first circular arc HI of the male rotor is positioned on an extension line which takes O1 as an original point and has an included angle alpha 1 with the joint line of O1O2, the first circular arc HI of the male rotor is tangent to a point H with the root circle Rg1 of the male rotor, and is tangent to a point J with the second circular arc IJ of the male rotor; arc radius r (hi) 0.07-0.1A;
the male rotor second arc IJ is tangent to the male rotor first arc HI at the point I and is tangent to the male rotor third arc JK at the point J; the arc radius r (hi) of the male rotor second arc IJ is 0.30-0.38A;
the center of a third arc JK of the male rotor is positioned on a straight line O1O2 and is positioned outside a pitch circle of the male rotor, and the arc radius R (JK) of the third arc JK of the male rotor is Rd1-Rt1-Kappa, wherein Kappa is the distance from the center of the arc JK to the pitch circle of the male rotor and is 0.001-0.012A;
the center of the fourth arc KL of the male rotor is on a straight line O1O2, the arc radius R (JK) of the fourth arc KL of the male rotor is 0.03-0.05A, and the arc radius R (JK) is tangent to a point k with the third arc JK of the male rotor;
the male rotor circular arc envelope line LM is generated by a female rotor first circular arc EF defined on the female rotor and is tangent to a point L with a male rotor fourth circular arc KL;
the circle center of the fifth circular arc MN of the male rotor is O1, namely the tooth root circular arc of the male rotor is tangent to the envelope line LM of the circular arc LM of the male rotor at the point M.
The first arc envelope line AB is a conjugate curve of a first arc HI of the male rotor; the envelope CD of the third arc of the female rotor is a conjugate curve of the third arc JK of the male rotor; a fourth arc envelope DE of the female rotor is a conjugate curve of a fourth arc KL of the male rotor;
the center of the first circular arc EF of the female rotor is on a straight line O2F and is positioned within a pitch circle of the female rotor, the radius R (EF) of the first circular arc EF of the female rotor is 0.010-0.035A, the radius Rd2 is R (EF) + Rt2-lambda, lambda is the distance from the center of the first circular arc EF of the female rotor to the pitch circle of the female rotor, and lambda takes a positive number and is tangent to the point E with the envelope DE of the fourth circular arc of the female rotor; tangent to the F point with the addendum arc FG of the female rotor;
the addendum arc FG of the female rotor is a conjugate curve of the fifth arc MN of the male rotor. To this end, the curves contained by the end face profiles of the female and male rotors are all constructed and expressed. The adjacent curves are connected smoothly and tangentially, the contact line is continuous, and the meshing line is completely closed. The sharp point in the tooth shape is thoroughly eliminated, the length of the contact line is moderate, and the area of the leakage triangle at the high-pressure side is small. During production, a driving belt (with the length of 2-3mm) is set near the pitch circle of the long edge of the male rotor and the female rotor, and reasonable gaps are left in the rest positions. The male and female rotors roll only without relative sliding, so that the abrasion can be reduced, the transmission is stable, and the noise and vibration are reduced. The female rotor has thick teeth and higher strength. The rotor area utilization coefficient is large.
As shown in fig. 2-3, the meshing line is continuous and has a good shape.
The distance between the highest point of the meshing line and the intersection point of the cavity of the male rotor and the cavity of the female rotor influences the size of the leakage triangle. As shown in fig. 3, line 12 is the intersection of the male and female rotor cavities, point 1 is the intersection of the female rotor and the rotor cavity, point 2 is the intersection of the male rotor and the rotor cavity, and point 3 is the highest point of the contact line. The triangle with curved sides formed by the points 1, 2 and 3 is the leakage triangle at the high pressure side.
The effect leakage triangle size is: radius r (EF) of first circular arc EF of female rotor, lambda (distance from center of first circular arc EF of female rotor to pitch circle of female rotor), radius r (jk) of fourth circular arc KL of male rotor.
By reasonably taking values, the leakage triangle is smaller, flat and has a large area utilization coefficient. The specific implementation is as follows:
the radius R (EF) and lambda of the first circular arc (EF) of the female rotor are reasonable values of the distance from the center of the circular arc (EF) to the pitch circle of the female rotor, so that the distance between the highest point of the meshing line and the intersection point of the cavity of the male rotor and the cavity of the female rotor is reduced, and the leakage triangle is small. The radius R (EF) ═ A (0.010-0.035), the value of lambda should be the minimum value under the condition that the conjugate curve (LM) can be normally generated, and the value of lambda is the general value of lambda ═ 0.010-0.5. And a fourth arc (KL) of the male rotor, the center of which is on the straight line O1O2, and the radius R (JK) of which is (0.03-0.05) A.
The above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (6)
1. A new twin-screw compressor rotor profile, comprising a male rotor profile (1) and a female rotor profile (2), characterized in that: the tooth profiles of the male rotor and the female rotor are all bilateral asymmetric tooth profiles taking arcs and arc envelope lines as basic constituent units.
2. The new twin-screw compressor rotor profile according to claim 1, characterized in that: the male rotor consists of six quadratic curve units, namely a male rotor first arc (HI), a male rotor second arc (IJ), a male rotor third arc (JK), a male rotor fourth arc (KL), a male rotor arc envelope Line (LM) and a male rotor fifth arc (MN);
the female rotor is composed of six quadratic curve units, namely a female rotor first arc envelope line (AB), a female rotor second arc envelope line (BC), a female rotor third arc envelope line (CD), a female rotor fourth arc envelope line (DE), a female rotor first arc (EF) and a female rotor addendum arc (FG).
3. The new twin-screw compressor rotor profile according to claim 2, characterized in that: taking O1 as the center of the male rotor, O2 as the center of the female rotor and A as the center distance of the male rotor and the female rotor; rd1, Rt1 and Rg1 are respectively a addendum circle radius, a pitch circle radius and a dedendum circle radius of the male rotor in sequence, and Rd2, Rt2 and Rg2 are respectively a addendum circle radius, a pitch circle radius and a dedendum circle radius of the female rotor in sequence, wherein Rd1 is (0.65-0.71) A, Rg1 is (0.39-0.5) A, Rg2 is A-Rg1, and Rd2 is A-Rd 1;
alpha 1 is the long side included angle of the male rotor, namely the included angle between a straight line O1H and a straight line O1O2, alpha 2 is the short side included angle of the male rotor, namely the included angle between a straight line O1N and a straight line O1O2, beta 1 is the long side included angle of the female rotor, namely the included angle between a straight line O2G and a straight line O1O2, and beta 2 is the short side included angle of the female rotor, namely the included angle between a straight line O1A and a straight line O1O 2; z1 represents the male rotor tooth count and Z2 represents the female rotor tooth count, then α 1+ α 2 is 360 °/Z1, β 1+ β 2 is 360 °/Z2, α 1: β 1 ═ Z2: z1, α 2: β 2 ═ Z2: z1, Rt1 ═ a × Z1/(Z1+ Z2), Rt2 ═ a × Z2/(Z1+ Z2).
4. The new twin-screw compressor rotor profile according to claim 2, characterized in that: the center O (HI) of the first circular arc (HI) of the male rotor is positioned on an extension line which takes O1 as an original point and has an included angle alpha 1 with the joint line of O1O2, the first circular arc (HI) of the male rotor is tangent to a male rotor root circle Rg1 at a point H and is tangent to a second circular arc (IJ) of the male rotor at a point J; arc radius r (hi) ═ 0.07-0.1) a;
the male rotor second arc (IJ) is tangent to the male rotor first arc (HI) at the point I and to the male rotor third arc (JK) at the point J; the arc radius r (hi) of the male rotor second arc (IJ) is (0.30-0.38) a;
the center of the third arc (JK) of the male rotor is on a straight line O1O2 and is positioned outside a pitch circle of the male rotor, and the arc radius R (JK) of the third arc (JK) of the male rotor is Rd1-Rt1-Kappa, wherein Kappa is the distance from the center of the arc (JK) to the pitch circle of the male rotor, and Kappa is (0.001-0.012) A;
the center of the fourth arc (KL) of the male rotor is on a straight line O1O2, the arc radius R (JK) of the fourth arc (KL) of the male rotor is (0.03-0.05) A, and the arc radius R (JK) is tangent to the third arc (JK) of the male rotor at a point k;
the male rotor circular arc envelope Line (LM) is generated by a first female rotor circular arc (EF) defined on the female rotor and is tangent to a point L with a fourth male rotor circular arc (KL);
the circle center of the fifth circular arc (MN) of the male rotor is O1, namely the tooth root circular arc of the male rotor is tangent to the point M with the envelope curve (LM) of the circular arc of the male rotor.
5. The new twin-screw compressor rotor profile according to claim 2, characterized in that: the first arc envelope (AB) is a conjugate curve of a first arc (HI) of the male rotor; the envelope Curve (CD) of the third circular arc of the female rotor is a conjugate curve of the third circular arc (JK) of the male rotor; the fourth arc envelope line (DE) of the female rotor is a conjugate curve of a fourth arc (KL) of the male rotor;
the center of the first female rotor arc (EF) is on a straight line O2F and is positioned within a female rotor pitch circle, the radius R (EF) of the first female rotor arc (EF) is (0.010-0.035) A, Rd2 is R (EF) + Rt2-lambda, lambda is the distance from the center of the first female rotor arc (EF) to the female rotor pitch circle, and lambda takes a positive number and is tangent to a fourth female rotor arc envelope (DE) at a point E; tangent to the point F with the addendum arc (FG);
and the addendum arc (FG) of the female rotor is a conjugate curve of a fifth arc (MN) of the male rotor.
6. The new twin-screw compressor rotor profile according to claim 1, characterized in that: the gear ratio of the male rotor to the female rotor is 4-6: 5 to 8.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210667566.4A CN114876796B (en) | 2022-06-14 | 2022-06-14 | Novel double-screw compressor rotor molded line |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210667566.4A CN114876796B (en) | 2022-06-14 | 2022-06-14 | Novel double-screw compressor rotor molded line |
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| CN114876796B CN114876796B (en) | 2023-05-12 |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1676935A (en) * | 2004-03-30 | 2005-10-05 | 李汗强 | Rotor tooth profile for helical-lobe compressor |
| JP2006214352A (en) * | 2005-02-03 | 2006-08-17 | Fu Sheng Industrial Co Ltd | Spiral rotator machine |
| CN202900668U (en) * | 2012-09-14 | 2013-04-24 | 上海齐耀螺杆机械有限公司 | Novel double screw compressor rotor |
| CN103291619A (en) * | 2013-07-03 | 2013-09-11 | 上海齐耀螺杆机械有限公司 | Double-screw compressor rotor molded line for oil injection |
| CN103603805A (en) * | 2013-11-21 | 2014-02-26 | 南京压缩机股份有限公司 | Rotor profile of double-screw compressor |
| CN110374871A (en) * | 2019-08-01 | 2019-10-25 | 上海艾群机械有限公司 | A kind of oil-free double-screw compressor molded lines of rotor |
-
2022
- 2022-06-14 CN CN202210667566.4A patent/CN114876796B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1676935A (en) * | 2004-03-30 | 2005-10-05 | 李汗强 | Rotor tooth profile for helical-lobe compressor |
| JP2006214352A (en) * | 2005-02-03 | 2006-08-17 | Fu Sheng Industrial Co Ltd | Spiral rotator machine |
| CN202900668U (en) * | 2012-09-14 | 2013-04-24 | 上海齐耀螺杆机械有限公司 | Novel double screw compressor rotor |
| CN103291619A (en) * | 2013-07-03 | 2013-09-11 | 上海齐耀螺杆机械有限公司 | Double-screw compressor rotor molded line for oil injection |
| CN103603805A (en) * | 2013-11-21 | 2014-02-26 | 南京压缩机股份有限公司 | Rotor profile of double-screw compressor |
| CN110374871A (en) * | 2019-08-01 | 2019-10-25 | 上海艾群机械有限公司 | A kind of oil-free double-screw compressor molded lines of rotor |
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| Publication number | Publication date |
|---|---|
| CN114876796B (en) | 2023-05-12 |
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