CN114876796B - Novel double-screw compressor rotor molded line - Google Patents
Novel double-screw compressor rotor molded line Download PDFInfo
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- CN114876796B CN114876796B CN202210667566.4A CN202210667566A CN114876796B CN 114876796 B CN114876796 B CN 114876796B CN 202210667566 A CN202210667566 A CN 202210667566A CN 114876796 B CN114876796 B CN 114876796B
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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
Abstract
A rotor profile of a novel double-screw compressor comprises a male rotor profile and a female rotor profile, wherein tooth profiles of the male rotor and the female rotor are double-sided asymmetric tooth profiles taking circular arcs and circular arc envelope lines as basic constituent units. The male rotor molded line and the female rotor molded line are obtained by analyzing the meshing envelope principle, double-sided asymmetric tooth shapes which take circular arcs and circular arc envelope lines as basic constituent units are all smooth and tangent connection between adjacent curves, contact lines are continuous, and meshing lines are completely closed. The rotor is streamline, so that the sharp point in the tooth shape is thoroughly eliminated, the contact line length is moderate, and the leakage triangle area at the high pressure side is small. During production and processing, a driving belt (the length is 2-3 mm) is arranged near the pitch circles of the long sides of the male and female rotors, and reasonable gaps are reserved in the rest parts. The male rotor and the female rotor do pure rolling without relative sliding, so that abrasion can be reduced, transmission is stable, and noise and vibration are reduced. The tooth thickness of the female rotor is thicker, and the strength is higher. 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 in particular relates to a novel rotor molded line of the double-screw compressor.
Background
The rotor of the double-screw compressor is a core component of the screw compressor, and the overall performance of the screw compressor is fundamentally determined by the rotor molded line. The profile of the male and female rotors consists of a plurality of sections of different primary or secondary mathematical curves such as circular arcs and circular arc envelopes, point (straight line) cycloids, ellipses and elliptical envelopes, parabolas and parabolic envelopes and the like, and each section of corresponding curve between the male and female rotors is obtained by analyzing according to the meshing envelope principle, and the different curves are connected in a tangent way and in smooth transition.
An excellent rotor profile is required to have smooth tooth profile (small flow loss), continuous contact line, as short as possible (good sealing effect), small leakage triangle (reduced internal leakage), small closed volume, good grinding processability (easy processing), and contemporary profile design has abandoned early point (straight line) cycloid (relatively sensitive to meshing property and processability) and all adopts smooth mathematical curves (such as circular arc, ellipse, parabola and the like), so that the sealing mode of the sealing side of the rotor is converted into an arc-arc sealing band from the traditional point (line) -arc sealing, internal leakage is reduced, and volumetric efficiency is improved. However, the traditional female rotor has thinner teeth, weaker tooth strength and poor processing.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides a novel double-screw compressor rotor molded line, and the novel double-screw compressor rotor molded line is designed for the existing double-screw compressor rotor with thinner teeth, weaker strength and poor processing, and has the advantages of thicker teeth, high strength, easy processing, stable transmission and low vibration and noise.
In order to achieve the above purpose, the invention is realized by the following technical scheme:
a rotor profile of a novel double-screw compressor comprises a male rotor profile and a female rotor profile, wherein tooth profiles of the male rotor and the female rotor are double-sided asymmetric tooth profiles taking circular arcs and circular arc envelope lines as basic constituent units.
Preferably, the male rotor is composed of six conic units of 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 conic units including 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 taken as a male rotor center, O2 is taken as a female rotor center, and A is taken as a female-male rotor center distance; rd1, rt1 and Rg1 are respectively the tooth top circle radius, the pitch circle radius and the tooth root circle radius of the male rotor in sequence, rd2, rt2 and Rg2 are respectively the tooth top circle radius, the pitch circle radius and the tooth root circle radius of the female rotor in sequence, wherein Rd1=0.65-0.71A, rg1=0.39-0.5A, rg2=A-Rd1 and Rd2=A-Rg1;
α1 is the angle between the long side of the male rotor, i.e. the angle between the straight line O1H and the straight line O1O2, α2 is the angle between the short side of the male rotor, i.e. the angle between the straight line O1N and the straight line O1O2, β1 is the angle between the long side of the female rotor, i.e. the angle between the straight line O2A and the straight line O1O2, and β2 is the angle between the short side of the female rotor, i.e. the angle between the straight line O2G and the straight line O1O 2; z1 is the number of teeth of the male rotor and Z2 is the number of teeth of the female rotor, then α1+α2=360°/Z1, β1+β2=360°/Z2, α1: β1=z2: z1, α2: β2=z2: z1, rt1=a×z1/(z1+z2), rt2=a×z2/(z1+z2).
Preferably, the center O of the first circular arc HI of the male rotor falls on an extension line taking O1 as an origin and having an included angle alpha 1 with the connecting line of O1O2, the first circular arc HI of the male rotor is tangent to the tooth root circle Rg1 of the male rotor at a point H, and the second circular arc IJ of the male rotor is tangent to the point I; arc radius R (HI) =0.07-0.1A;
the second arc IJ of the male rotor is tangent to the first arc HI of the male rotor at a point I, and is tangent to the third arc JK of the male rotor at a point J; the arc radius R (IJ) =0.30-0.38A of the second arc IJ of the male rotor;
the center of the third arc JK of the male rotor is positioned outside the pitch circle of the male rotor and is positioned at a straight line O1O2, and the arc radius R (JK) =Rd1-Rt 1-kappa of the third arc JK of the male rotor, wherein kappa is the distance from the center of the arc JK to the pitch circle of the male rotor, and kappa=0.001-0.012A;
the center of the fourth arc KL of the male rotor is on a straight line O1O2, and the arc radius R (KL) =0.03-0.05A of the fourth arc KL of the male rotor is tangent to the third arc JK of the male rotor at a k point;
the male rotor arc envelope line LM is generated by a female rotor first arc EF defined on the female rotor and is tangential to a male rotor fourth arc KL at a point L;
the center of the fifth arc MN of the male rotor is O1, namely the root arc of the male rotor and the arc envelope LM of the male rotor are tangent to the point M.
Preferably, the first arc envelope line AB is a conjugate curve of the first arc HI of the male rotor; the third circular arc envelope line CD 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 the fourth arc KL of the male rotor;
the center of the first circular arc EF of the female rotor is positioned on a straight line O2F and is positioned in the pitch circle of the female rotor, the radius R (EF) =0.010-0.035A, rd2=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, lambda is a positive number, and the lambda is tangential to the envelope line DE of the fourth circular arc of the female rotor at the E point; tangent to the tooth top arc FG of the female rotor at the point F;
the tooth top arc FG of the female rotor is a conjugate curve of the fifth arc MN of the male rotor.
Preferably, the ratio of the number of teeth of the male rotor to the number of teeth of the female rotor is 4-6: 5 to 8.
The invention provides a novel rotor molded line of a double-screw compressor. The beneficial effects are as follows: the male rotor molded line and the female rotor molded line are obtained by analyzing the meshing envelope principle, double-sided asymmetric tooth shapes which take circular arcs and circular arc envelope lines as basic constituent units are all smooth and tangent connection between adjacent curves, contact lines are continuous, and the meshing lines are completely closed. The rotor is streamline, so that the sharp point in the tooth shape is thoroughly eliminated, the contact line length is moderate, and the leakage triangle area at the high pressure side is small. During production and processing, a driving belt is arranged near the pitch circles of the long sides of the male and female rotors, and reasonable gaps are reserved in the rest parts. The male rotor and the female rotor do pure rolling without relative sliding, so that abrasion can be reduced, transmission is stable, and noise and vibration are reduced. The tooth thickness of the female rotor is thicker, and the strength is higher. The rotor area utilization coefficient is large.
Drawings
In order to more clearly illustrate the invention or the technical solutions in the prior art, the drawings used in the description of the prior art will be briefly described below.
FIG. 1 is a schematic view of a rotor profile engagement state structure of a twin screw compressor of the present invention;
FIG. 2 is a meshing line diagram of the present invention;
FIG. 3 is a leakage triangle of 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 clearly and completely described below with reference to the accompanying drawings.
As shown in fig. 1 to 3, a novel rotor profile of a twin-screw compressor comprises a male rotor profile 1 and a female rotor profile 2, and the tooth ratio of the male rotor to the female rotor is 4-6: 5 to 8; 4 can be selected according to low, medium and high exhaust pressure conditions: 5. 4: 6. 5: 6. 5: 7. 6: 7. 6:8, etc.
The tooth shapes of the male rotor and the female rotor are bilateral asymmetric tooth shapes which take circular arcs and circular arc envelope lines as basic constituent units.
The male rotor consists of six conic units of a first circular arc HI of the male rotor, a second circular arc IJ of the male rotor, a third circular arc JK of the male rotor, a fourth circular arc KL of the male rotor, a circular arc envelope LM of the male rotor and a fifth circular arc MN of the male rotor;
the female rotor is composed of six conic units including a female rotor first arc envelope AB, a female rotor second arc envelope BC, a female rotor third arc envelope CD, a female rotor fourth arc envelope DE, a female rotor first arc EF and a female rotor addendum arc FG.
O1 is taken as the center of a male rotor, O2 is taken as the center of a female rotor, and A is the center distance between the male rotor and the female rotor; rd1, rt1 and Rg1 are respectively the tooth top circle radius, the pitch circle radius and the tooth root circle radius of the male rotor in sequence, rd2, rt2 and Rg2 are respectively the tooth top circle radius, the pitch circle radius and the tooth root circle radius of the female rotor in sequence, wherein Rd1=0.65-0.71A, rg1=0.39-0.5A, rg2=A-Rd1 and Rd2=A-Rg1;
α1 is the angle between the long side of the male rotor, i.e. the angle between the straight line O1H and the straight line O1O2, α2 is the angle between the short side of the male rotor, i.e. the angle between the straight line O1N and the straight line O1O2, β1 is the angle between the long side of the female rotor, i.e. the angle between the straight line O2A and the straight line O1O2, and β2 is the angle between the short side of the female rotor, i.e. the angle between the straight line O2G and the straight line O1O 2; z1 is the number of teeth of the male rotor and Z2 is the number of teeth of the female rotor, then α1+α2=360°/Z1, β1+β2=360°/Z2, α1: β1=z2: z1, α2: β2=z2: z1, rt1=a×z1/(z1+z2), rt2=a×z2/(z1+z2).
The circle center O of the first circular arc HI of the male rotor is positioned on an extension line taking O1 as an origin and having an included angle alpha 1 with the connecting line of O1O2, the tangent of the first circular arc HI of the male rotor with the tooth root circle Rg1 of the male rotor is tangent to the H point, and the tangent of the first circular arc HI of the male rotor with the second circular arc IJ of the male rotor is tangent to the I point; arc radius R (HI) =0.07-0.1A;
the second arc IJ of the male rotor is tangent to the first arc HI of the male rotor at a point I, and is tangent to the third arc JK of the male rotor at a point J; the arc radius R (IJ) =0.30-0.38A of the second arc IJ of the male rotor;
the center of the third arc JK of the male rotor is positioned outside the pitch circle of the male rotor and is positioned at the straight line O1O2, and the arc radius R (JK) =Rd1-Rt 1-kappa of the third arc JK of the male rotor, wherein kappa is the distance from the center of the arc JK to the pitch circle of the male rotor, and kappa=0.001-0.012A;
the circle center of the fourth arc KL of the male rotor is on a straight line O1O2, and the arc radius R (KL) =0.03-0.05A of the fourth arc KL of the male rotor is tangent to the third arc JK of the male rotor at a k point;
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 tangential to a male rotor fourth circular arc KL at a point L;
the center of the fifth arc MN of the male rotor is O1, namely the arc of the tooth root of the male rotor and the arc envelope LM of the male rotor are tangent to the point M.
The first arc envelope line AB is a conjugate curve of a first arc HI of the male rotor; the third circular arc envelope line CD 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 the fourth arc KL of the male rotor;
the center of the first circular arc EF of the female rotor is positioned on a straight line O2F and is positioned in the pitch circle of the female rotor, the radius R (EF) =0.010-0.035A, rd2=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, lambda is a positive number, and is tangential to the envelope line DE of the fourth circular arc of the female rotor at the E point; tangent to the tooth top arc FG of the female rotor at the point F;
the tooth top arc FG of the female rotor is the conjugate curve of the fifth arc MN of the male rotor. The curves contained in the end face tooth shapes of the female rotor and the male rotor are all constructed and expressed. The adjacent curves are connected in a smooth and tangential manner, the contact lines are 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 on the high pressure side is small. During production and processing, a driving belt (the length is 2-3 mm) is arranged near the pitch circles of the long sides of the male and female rotors, and reasonable gaps are reserved in the rest parts. The male rotor and the female rotor do pure rolling without relative sliding, so that abrasion can be reduced, transmission is stable, and noise and vibration are reduced. The tooth thickness of the female rotor is thicker, and the strength is higher. The rotor area utilization coefficient is large.
As shown in fig. 2-3, the line of engagement is continuous and has a good shape.
The distance between the highest point of the meshing line and the intersection point of the male rotor cavity and the female rotor cavity influences the size of the leakage triangle. As shown in fig. 3, the straight line 12 is the intersecting line of the male and female rotors, the point 1 is the intersecting line of the female rotor and the rotor cavities, the point 2 is the intersecting line of the male rotor and the rotor cavities, and the point 3 is the highest point of the contact line. The curved triangle surrounded by point 1, point 2 and point 3 is the high pressure side leakage triangle.
The impact leakage triangle size is: radius R (EF) of the first circular arc EF of the female rotor, lambda (distance from the center of the first circular arc EF of the female rotor to the pitch circle of the female rotor), radius R (JK) of the fourth circular arc KL of the male rotor.
Through reasonable value, can make the leakage triangle less, flat and area utilization coefficient is big. The specific implementation is as follows:
the radius R (EF) of the first circular arc (EF) of the female rotor is a reasonable value 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 female rotor is reduced, and the leakage triangle is small. The radius R (EF) = (0.010-0.035) a, the lambda value should be the minimum value under the condition that the conjugate curve (LM) can be normally generated, and the lambda= (0.010-0.5) is general. And a fourth arc (KL) of the male rotor, the center of which is on a straight line O1O2, and the radius R (JK) = (0.03-0.05) A.
The above embodiments are only for illustrating the technical solution of the present invention, and are not limiting; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.
Claims (3)
1. The utility model provides a novel double screw compressor rotor molded lines, includes male rotor molded lines (1) and female rotor molded lines (2), its characterized in that: the tooth shapes of the male rotor and the female rotor are bilateral asymmetric tooth shapes which take circular arcs and circular arc envelope lines as basic constituent units;
the male rotor consists of six conic units of 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 curve (LM) and a male rotor fifth arc (MN);
the female rotor consists of six conic units including a female rotor first arc envelope curve (AB), a female rotor second arc envelope curve (BC), a female rotor third arc envelope Curve (CD), a female rotor fourth arc envelope curve (DE), a female rotor first arc (EF) and a female rotor tooth top arc (FG);
o1 is taken as the center of a male rotor, O2 is taken as the center of a female rotor, and A is the center distance between the male rotor and the female rotor; rd1, rt1 and Rg1 are respectively the tooth top radius, the pitch radius and the tooth root radius of the male rotor in sequence, rd2, rt2 and Rg2 are respectively the tooth top radius, the pitch radius and the tooth root radius of the female rotor in sequence, alpha 1 is the included angle of the long side of the male rotor, namely the included angle of a straight line O1H and a straight line O1O2, and alpha 2 is the included angle of the short side of the male rotor, namely the included angle of a straight line O1N and a straight line O1O 2;
the circle center O of the first circular arc (HI) of the male rotor is positioned on an extension line taking O1 as an origin and an included angle alpha 1 with the connecting line of O1O2, the first circular arc (HI) of the male rotor is tangent to the tooth root circle Rg1 of the male rotor at a point H, and the second circular arc (IJ) of the male rotor is tangent to the point I; arc radius R (HI) = (0.07-0.1) a;
the second arc (IJ) of the male rotor is tangential to the first arc (HI) of the male rotor at the point I and tangential to the third arc (JK) of the male rotor at the point J; arc radius R (IJ) = (0.30-0.38) a of the second arc (IJ) of the male rotor;
the center of the third circular arc (JK) of the male rotor is positioned outside the pitch circle of the male rotor and is positioned at a straight line O1O2, and the circular arc radius R (JK) =Rd1-Rt 1-kappa of the third circular arc (JK) of the male rotor, wherein kappa is the distance from the center of the circular arc (JK) to the pitch circle of the male rotor, and kappa= (0.001-0.012) A;
the circle center of the fourth arc (KL) of the male rotor is on a straight line O1O2, and the arc radius R (KL) = (0.03-0.05) A of the fourth arc (KL) of the male rotor is tangent to the third arc (JK) of the male rotor at a k point;
the male rotor arc envelope curve (LM) is generated by a female rotor first arc (EF) defined on the female rotor and is tangential to a male rotor fourth arc (KL) at a point L;
the center of the fifth arc (MN) of the male rotor is O1, namely the root arc of the male rotor is tangent to the M point with the arc envelope (LM) of the male rotor;
the first arc envelope curve (AB) is a conjugate curve of a first arc (HI) of the male rotor; the third circular arc envelope Curve (CD) of the female rotor is a conjugate curve of the third circular arc (JK) of the male rotor; the fourth arc envelope curve (DE) of the female rotor is a conjugate curve of the fourth arc (KL) of the male rotor;
the center of the first circular arc (EF) of the female rotor is positioned on a straight line O2F and is positioned in the pitch circle of the female rotor, the radius R (EF) = (0.010-0.035) A of the first circular arc (EF) of the female rotor, rd2=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, lambda takes a positive number and is tangent to the fourth circular arc envelope line (DE) of the female rotor at the E point; tangent to the tip arc (FG) of the female rotor at the point F;
the tooth top arc (FG) of the female rotor is a conjugate curve of the fifth arc (MN) of the male rotor.
2. A new twin screw compressor rotor profile as defined in claim 1, wherein: wherein Rd1= (0.65-0.71) A, rg1= (0.39-0.5) A, rg2=A-Rd1, rd2=A-Rg1;
beta 1 is the included angle of the long side of the female rotor, namely the included angle of a straight line O2A and a straight line O1O2, and beta 2 is the included angle of the short side of the female rotor, namely the included angle of a straight line O2G and a straight line O1O 2; z1 is the number of teeth of the male rotor and Z2 is the number of teeth of the female rotor, then α1+α2=360°/Z1, β1+β2=360°/Z2, α1: β1=z2: z1, α2: β2=z2: z1, rt1=a×z1/(z1+z2), rt2=a×z2/(z1+z2).
3. A new twin screw compressor rotor profile as defined in claim 1, wherein: the tooth ratio of the male rotor to the female rotor is 4-6: 5 to 8.
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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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| CN202210667566.4A CN114876796B (en) | 2022-06-14 | 2022-06-14 | Novel double-screw compressor rotor molded line |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN100351523C (en) * | 2004-03-30 | 2007-11-28 | 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 |
| CN103291619B (en) * | 2013-07-03 | 2015-06-17 | 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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