CN114320921B - Design method of double-head claw pump rotor molded line - Google Patents
Design method of double-head claw pump rotor molded line Download PDFInfo
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Abstract
The invention relates to a design method of a double-head claw pump rotor molded line, which comprises a rotor 1 and a rotor 2, wherein the rotor 1 and the rotor 2 respectively rotate about a rotor shaft rotation center O of the rotor 1 And rotor shaft rotation center O 2 Symmetrical; the upper half rotor profile of rotor 1 is formed by point meshing cycloid a 1 b 1 Tooth top pair rolling arc b 1 c 1 Arc c of transition 1 d 1 Arc d of transition 1 e 1 And tooth bottom pair rolling arc e 1 f 1 The upper half rotor profile of the rotor 2 is formed by point meshing cycloid a 2 b 2 Arc b of opposite rolling of tooth bottom 2 c 2 Arc envelope c 2 d 2 Arc envelope d 2 e 2 And tooth tip to rolling arc e 2 f 2 Constructing; a of the rotor 1 and rotor 2 1 b 1 And a 2 Engagement, b 1 And a 2 b 2 Engagement, b 1 c 1 And b 2 c 2 Engagement, c 1 d 1 And c 2 d 2 Engaged d 1 e 1 And d 2 e 2 Engagement e 1 f 1 And e 2 f 2 Engagement. The claw pump rotor molded line ensures that the claw pump rotor is correctly meshed when synchronously rotating in different directions, solves the problems of complex structure composition and low volume utilization coefficient of the existing claw pump rotor, and improves the working performance of the claw pump.
Description
Technical Field
The invention relates to the technical field of mechanical engineering, in particular to a design method of a double-head claw pump rotor molded line.
Background
The claw pump is used as a rotary vacuum compressor, has the advantages of compact structure, reliable operation, long mechanical life, small vibration noise, dry oil-free compression and the like, is widely applied to various fields of food, medicine, chemical industry and the like, and has good application prospect in low-pressure gas transmission. Particularly, the characteristic of oil-free compression is good in performance and is of great concern in a hydrogen return system of a fuel cell, so that the method has great potential in the future hydrogen energy application field.
The claw pump consists of a pair of intermeshing rotors and a 8-shaped compression cavity, and the synchronous and different-direction rotation of the rotors drives the periodical change of the volume of gas in the compression cavity to realize the processes of air suction, compression and air discharge. Therefore, the claw rotor is used as a core component of the claw pump, and the compression performance of the claw pump, such as air tightness, volume utilization rate, working efficiency and service life, is directly affected by the quality of the molded line design. The pair of meshed double-end rotor molded lines are formed by multiple sections of curves, each section of curve is correspondingly meshed in the synchronous and opposite rotation process, and the molded line of each rotor is divided into an upper part and a lower part and is symmetrical about a rotation center. However, the existing double-end claw type rotor molded line has the defects of complex structure composition, high processing difficulty, high cost, low volume utilization rate and the like.
Disclosure of Invention
Aiming at the defects of the prior art, the patent application aims to provide a design method of a double-head claw pump rotor molded line so as to ensure that claw pump rotors are correctly meshed in synchronous opposite rotation and solve the problems of complex structure composition and low volume utilization coefficient of the claw pump rotors in the prior art, thereby greatly improving the working performance of the claw pump.
In order to solve the technical problems, the invention adopts the following technical scheme:
a design method of a double-head claw pump rotor molded line comprises a rotor 1 and a rotor 2, wherein the rotor 1 and the rotor 2 respectively rotate about a rotor shaft rotation center O of the rotor 1 And rotor shaft rotation center O 2 Symmetrical;
the upper half rotor profile of the rotor 1 is formed by point meshing cycloid a 1 b 1 Tooth top pair rolling arc b 1 c 1 Arc c of transition 1 d 1 Arc d of transition 1 e 1 And tooth bottom pair rolling arc e 1 f 1 The upper half rotor profile of the rotor 2 is formed by point meshing cycloid a 2 b 2 Arc b of opposite rolling of tooth bottom 2 c 2 Arc envelope c 2 d 2 Arc envelope d 2 e 2 And tooth tip to rolling arc e 2 f 2 Constructing;
the rotor 1 and the rotor 2 each rotate around a rotor shaft rotation center O 1 And rotor shaft rotation center O 2 In the synchronous and opposite rotation process, the point meshing cycloid a 1 b 1 And point a 2 Engagement, point b 1 Cycloid a meshed with point 2 b 2 Engaged, tooth top pairs rolling arc b 1 c 1 Arc b opposite to tooth bottom 2 c 2 Engagement, transition arc c 1 d 1 And the arc envelope line c 2 d 2 Engagement, transition arc d 1 e 1 And the circular arc envelope line d 2 e 2 Meshing, tooth bottom-to-rolling arc e 1 f 1 Arc e of rolling circle opposite to tooth top 2 f 2 Engagement;
the point b 1 Point a 2 Point a is the sharp point 1 Point c 1 Point d 1 Point e 1 Point f 1 Point b 2 Point c 2 Point d 2 Point e 2 Point f 2 Are common tangent points of two adjacent sections of curves to form a smooth curve, so that the meshing process is stable;
the pitch radius of the rotor 1 is r 1 The pitch radius of the rotor 2 is r 2 Rotor 1 and rotor 2 are synchronously meshed, and meshing parameter transmission ratio i=r 1 /r 2 =1, the pitch radii of rotor 1 and rotor 2 are the same, i.e. r 1 ＝r 2 And center distance a=r 1 +r 2 ＝2r 1 。
Further, point meshing cycloid a 1 b 1 Satisfies the following formula:
x ab1 ＝acost ab -bcosct ab
y ab1 ＝-(asint ab -bsinct ab )
point meshing cycloid a 2 b 2 Satisfies the following formula:
x ab2 ＝acost ab -bcosct ab
y ab2 ＝asint ab -bsinct ab
wherein a is the distance from the center of the circle to the center of the base circle, a=a, and the radius of the circle b=r h ，A、R h Known, wherein R is h Is the radius of the top circle of the tooth,c＝a/r 1 ＝2。
further, the tooth top pairs the rolling arc b 1 c 1 Satisfies the following formula:
x bc1 ＝r bc cost bc
y bc1 ＝r bc sint bc
tooth bottom pair rolling arc b 2 c 2 Satisfies the following formula:
x bc2 ＝(A-r bc )cost bc
y bc2 ＝(A-r bc )sint bc
wherein r is bc B is 1 c 1 Radius of arc r bc ＝R h ；t bc ∈(0,α 1 )，α 1 B is 1 c 1 Arc of a circle, alpha 1 Is known.
Further, the transition arc c 1 d 1 Satisfies the following formula:
x cd1 ＝(r bc -r cd )cosα 1 +r cd cost cd
y cd1 ＝(r bc -r cd )sinα 1 +r cd sint cd
arc envelope c 2 d 2 Satisfies the following formula:
wherein r is cd C is 1 d 1 Is arranged on the inner side of the circular arc,t cd ∈(α 1 ,α 1 +α 2 )，α 2 c is 1 d 1 Arc of a circle, alpha 2 Is known.
Further, the transition arc d 1 e 1 Satisfies the following formula:
arc envelope d 2 e 2 Satisfies the following formula:
wherein, the liquid crystal display device comprises a liquid crystal display device,r de is d 1 e 1 Is arranged on the inner side of the circular arc,t de ∈(α 1 +α 2 ,π-α 4 )。
further, the tooth bottom is opposite to the rolling arc e 1 f 1 Satisfies the following formula:
x ef1 ＝r ef cost ef
y ef1 ＝r ef sint ef
tooth top pair rolling arc e 2 f 2 Satisfies the following formula:
x ef2 ＝(A-r ef )cost ef
y ef2 ＝(A-r ef )sint ef
wherein r is ef E is 1 f 1 Radius of arc r ef ＝A-r bc ；t ef ∈(π-α 4 ,π)，α 4 E is 1 f 1 Arc of a circle, alpha 4 Is known.
In summary, the double-head claw pump rotor molded line provided by the invention is only composed of cycloids, circular arcs and corresponding meshing curves, and can realize correct meshing and smooth operation of rotor pairs so as to ensure gas compression and reduce internal leakage. Compared with the existing claw pump rotor, the air tightness and the volume utilization coefficient of the pump are improved, the pumping speed of the claw pump is further improved, and the claw pump has strong practicability; meanwhile, the method has important significance for enriching the type of rotor molded lines of the claw pump and promoting the development of the claw pump.
Drawings
Fig. 1 is a schematic structural view of a double-ended claw pump rotor profile according to the present invention.
FIG. 2 is a view of the claw-type pump suction stage of FIG. 1, in which the rotor chamber is in communication with the suction port, thereby effecting the suction process of the compression chamber.
Fig. 3 is a diagram of the transport phase of the claw pump of fig. 1, wherein the rotor chamber air chamber is not communicated with the air suction port and the air exhaust port, and the volume of air is unchanged, so that the transport process of the compression chamber is realized.
Fig. 4 is a diagram of the compression stage of the claw-pump of fig. 1, in which the inter-rotor air chamber is not communicated with the air inlet and the air outlet, but the volume of the inter-rotor air chamber is reduced, so that the compression process of the compression chamber is realized.
Fig. 5 is a diagram of the discharge stage of the claw pump of fig. 1, in which the rotor chamber is in communication with the discharge port, thereby effecting the discharge process of the compression chamber.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings. In the description of the present invention, it should be understood that the azimuth or positional relationship indicated by the azimuth words such as "upper, lower" and "top, bottom", etc. are generally based on the azimuth or positional relationship shown in the drawings, and are merely for convenience of description and simplification of the description, and these azimuth words do not indicate or imply that the apparatus or element to be referred to must have a specific azimuth or be constructed and operated in a specific azimuth, without limiting the scope of protection of the present invention; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.
1-5, a design method of a double-head claw pump rotor molded line comprises a rotor 1 and a rotor 2, wherein the rotor 1 and the rotor 2 respectively rotate about a rotor shaft rotation center O 1 And rotor shaft rotation center O 2 Symmetrical;
the upper half rotor profile of the rotor 1 is formed by point meshing cycloid a 1 b 1 Tooth top pair rolling arc b 1 c 1 Arc c of transition 1 d 1 Arc d of transition 1 e 1 And tooth bottom pair rolling arc e 1 f 1 The upper half rotor profile of the rotor 2 is formed by point meshing cycloid a 2 b 2 Arc b of opposite rolling of tooth bottom 2 c 2 Arc envelope c 2 d 2 Arc envelope d 2 e 2 And tooth tip to rolling arc e 2 f 2 Constructing;
the rotor 1 and the rotor 2 each rotate around a rotor shaft rotation center O 1 And rotor shaft rotation center O 2 Synchronous and anisotropicDuring rotation, point meshing cycloid a 1 b 1 And point a 2 Engagement, point b 1 Cycloid a meshed with point 2 b 2 Engaged, tooth top pairs rolling arc b 1 c 1 Arc b opposite to tooth bottom 2 c 2 Engagement, transition arc c 1 d 1 And the arc envelope line c 2 d 2 Engagement, transition arc d 1 e 1 And the circular arc envelope line d 2 e 2 Meshing, tooth bottom-to-rolling arc e 1 f 1 Arc e of rolling circle opposite to tooth top 2 f 2 Engagement;
the point b 1 Point a 2 Point a is the sharp point 1 Point c 1 Point d 1 Point e 1 Point f 1 Point b 2 Point c 2 Point d 2 Point e 2 Point f 2 Are common tangent points of two adjacent sections of curves to form a smooth curve, so that the meshing process is stable;
the pitch radius of the rotor 1 is r 1 The pitch radius of the rotor 2 is r 2 Rotor 1 and rotor 2 are synchronously meshed, and meshing parameter transmission ratio i=r 1 /r 2 =1, the pitch radii of rotor 1 and rotor 2 are the same, i.e. r 1 ＝r 2 And center distance a=r 1 +r 2 ＝2r 1 。
Further, point meshing cycloid a 1 b 1 Satisfies the following formula:
x ab1 ＝acost ab -bcosct ab
y ab1 ＝-(asint ab -bsinct ab )
point meshing cycloid a 2 b 2 Satisfies the following formula:
x ab2 ＝acost ab -bcosct ab
y ab2 ＝asint ab -bsinct ab
wherein a is the distance from the center of the circle to the center of the base circle, a=a, and the radius of the circle b=r h ，A、R h Known, wherein R is h Is the radius of the top circle of the tooth,c＝a/r 1 ＝2。
further, the tooth top pairs the rolling arc b 1 c 1 Satisfies the following formula:
x bc1 ＝r bc cost bc
y bc1 ＝r bc sint bc
tooth bottom pair rolling arc b 2 c 2 Satisfies the following formula:
x bc2 ＝(A-r bc )cost bc
y bc2 ＝(A-r bc )sint bc
wherein r is bc B is 1 c 1 Radius of arc r bc ＝R h ；t bc ∈(0,α 1 )，α 1 B is 1 c 1 Arc of a circle, alpha 1 Is known.
Further, the transition arc c 1 d 1 Satisfies the following formula:
x cd1 ＝(r bc -r cd )cosα 1 +r cd cost cd
y cd1 ＝(r bc -r cd )sinα 1 +r cd sint cd
arc envelope c 2 d 2 Satisfies the following formula:
wherein r is cd C is 1 d 1 Is arranged on the inner side of the circular arc,t cd ∈(α 1 ,α 1 +α 2 )，α 2 c is 1 d 1 Arc of a circle, alpha 2 Is known.
Further, the transition arc d 1 e 1 Satisfies the following formula:
arc envelope d 2 e 2 Satisfies the following formula:
wherein r is de Is d 1 e 1 Is arranged on the inner side of the circular arc,t de ∈(α 1 +α 2 ,π-α 4 )。
further, the tooth bottom is opposite to the rolling arc e 1 f 1 Satisfies the following formula:
x ef1 ＝r ef cost ef
y ef1 ＝r ef sint ef
tooth top pair rolling arc e 2 f 2 Satisfies the following formula:
x ef2 ＝(A-r ef )cost ef
y ef2 ＝(A-r ef )sint ef
wherein r is ef E is 1 f 1 Radius of arc r ef ＝A-r bc ；t ef ∈(π-α 4 ,π)，α 4 E is 1 f 1 Arc of a circle, alpha 4 Is known.
The verification of the meshing operation state of the claw-type pump rotor molded lines under different corners in fig. 2-5 shows that the proposed claw-type pump rotor molded lines are reasonable in design, the correct meshing of the driving rotor 1 and the driven rotor 2 in the operation process can be effectively ensured, the air inlet 4, the air outlet 5 and the compression cavity 3 are matched, the air inlet, compression and exhaust processes of air can be effectively realized, the precise meshing of the rotors prevents high-pressure air from leaking into the low-pressure air inlet end in the air compression process, and the air tightness of the compression cavity is improved. And because the volume of the compression cavity occupied by the rotor is smaller, the higher volume utilization coefficient is ensured, and the performance of the claw pump is improved.
The black hatching in fig. 2 to 5 indicates the inter-rotor air chambers.
FIG. 2 shows a claw-type pump suction stage diagram, in which the rotor chamber is connected to the suction port, so as to realize suction of the compression chamber.
Fig. 3 shows a transport stage diagram of the claw pump, in which the rotor chamber is not communicated with the air inlet and the air outlet, and the volume of the air is unchanged, so that the transport process of the compression chamber is realized.
Fig. 4 shows a claw pump compression stage diagram, in which the rotor air chamber is not communicated with the air suction port and the air exhaust port, but the volume of the rotor air chamber is reduced, so that the compression process of the compression chamber is realized.
Fig. 5 shows a diagram of the exhaust stage of the claw pump, in which the rotor chamber is connected to the exhaust port, so as to realize the exhaust process of the compression chamber.
Finally, it should be noted that: various modifications and alterations of this invention may be made by those skilled in the art without departing from the spirit and scope of this invention. Thus, it is intended that the present invention also include such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.
Claims (6)
1. The design method of the double-head claw pump rotor molded line is characterized by comprising a rotor 1 and a rotor 2, wherein the rotor 1 and the rotor 2 respectively rotate about a rotor shaft rotation center O of the rotor 1 and the rotor 2 1 And rotor shaft rotation center O 2 Symmetrical;
the upper half rotor profile of the rotor 1 is formed by point meshing cycloid a 1 b 1 Tooth top pair rolling arc b 1 c 1 Arc c of transition 1 d 1 Arc d of transition 1 e 1 And tooth bottom pair rolling arc e 1 f 1 The upper half rotor profile of the rotor 2 is formed by point meshing cycloid a 2 b 2 Arc b of opposite rolling of tooth bottom 2 c 2 Arc envelope c 2 d 2 Arc envelope d 2 e 2 And tooth tip to rolling arc e 2 f 2 Constructing;
the rotor 1 and the rotor 2 each rotate around a rotor shaft rotation center O 1 And rotor shaft rotation center O 2 In the synchronous and opposite rotation process, the point meshing cycloid a 1 b 1 And point a 2 Engagement, point b 1 Cycloid a meshed with point 2 b 2 Engaged, tooth top pairs rolling arc b 1 c 1 Arc b opposite to tooth bottom 2 c 2 Engagement, transition arc c 1 d 1 And the arc envelope line c 2 d 2 Engagement, transition arc d 1 e 1 And the circular arc envelope line d 2 e 2 Meshing, tooth bottom-to-rolling arc e 1 f 1 Arc e of rolling circle opposite to tooth top 2 f 2 Engagement;
the point b 1 Point a 2 Point a is the sharp point 1 Point c 1 Point d 1 Point e 1 Point f 1 Point b 2 Point c 2 Point d 2 Point e 2 Point f 2 Are common tangent points of two adjacent sections of curves to form a smooth curve, so that the meshing process is stable;
the pitch radius of the rotor 1 is r 1 The pitch radius of the rotor 2 is r 2 Rotor 1 and rotor 2 are synchronously meshed, and meshing parameter transmission ratio i=r 1 /r 2 =1, the pitch radii of rotor 1 and rotor 2 are the same, i.e. r 1 ＝r 2 And center distance a=r 1 +r 2 ＝2r 1 。
2. The method for designing a double-ended claw pump rotor profile according to claim 1, wherein the point meshing cycloid a 1 b 1 Satisfies the following formula:
x ab1 ＝acost ab -bcosct ab
y ab1 ＝-(asint ab -bsinct ab )
point meshing cycloid a 2 b 2 Satisfies the following formula:
x ab2 ＝acost ab -bcosct ab
y ab2 ＝asint ab -bsinct ab
wherein a is the distance from the center of the circle to the center of the base circle, a=a, and the radius of the circle b=r h ，A、R h Known, wherein R is h Is the radius of the top circle of the tooth,c＝a/r 1 ＝2。
3. the method for designing a double-ended claw pump rotor profile according to claim 1, wherein the tooth tip-to-rolling arc b 1 c 1 Satisfies the following formula:
x bc1 ＝r bc cost bc
y bc1 ＝r bc sint bc
tooth bottom pair rolling arc b 2 c 2 Satisfies the following formula:
x bc2 ＝(A-r bc )cost bc
y bc2 ＝(A-r bc )sint bc
wherein r is bc B is 1 c 1 Radius of arc r bc ＝R h ；t bc ∈(0,α 1 )，α 1 B is 1 c 1 Arc of a circle, alpha 1 Is known.
4. A method of designing a double-ended claw pump rotor profile as claimed in claim 3, wherein the transition arc c is 1 d 1 Satisfies the following formula:
x cd1 ＝(r bc -r cd )cosα 1 +r cd cost cd
y cd1 ＝(r bc -r cd )sinα 1 +r cd sint cd
arc envelope c 2 d 2 Satisfies the following formula:
wherein r is cd C is 1 d 1 Is arranged on the inner side of the circular arc,t cd ∈(α 1 ,α 1 +α 2 )，α 2 c is 1 d 1 Arc of a circle, alpha 2 Is known; r is (r) ef E is 1 f 1 Radius of arc r ef ＝A-r bc 。
5. The method for designing a double-ended claw pump rotor profile as recited in claim 4, wherein the transition arc d 1 e 1 Satisfies the following formula:
arc envelope d 2 e 2 Satisfies the following formula:
wherein r is de Is d 1 e 1 Is arranged on the inner side of the circular arc,t de ∈(α 1 +α 2 ,π-α 4 )。
6. the method for designing a double-ended claw pump rotor profile according to claim 1, wherein the tooth bottom-to-rolling arc e 1 f 1 Satisfies the following formula:
x ef1 ＝r ef cost ef
y ef1 ＝r ef sint ef
tooth top pair rolling arc e 2 f 2 Satisfies the following formula:
x ef2 ＝(A-r ef )cost ef
y ef2 ＝(A-r ef )sint ef
wherein r is ef E is 1 f 1 Radius of arc r ef ＝A-r bc ；t ef ∈(π-α 4 ,π)，α 4 E is 1 f 1 Arc of a circle, alpha 4 Is known.
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| CN202111656647.6A CN114320921B (en) | 2021-12-30 | 2021-12-30 | Design method of double-head claw pump rotor molded line |
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| CN202111656647.6A CN114320921B (en) | 2021-12-30 | 2021-12-30 | Design method of double-head claw pump rotor molded line |
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| CN114320921B true CN114320921B (en) | 2023-08-25 |
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| CN1676936A (en) * | 2004-03-30 | 2005-10-05 | 肖文伟 | Rotor tooth-profile for screw pump |
| CN105756929A (en) * | 2016-04-22 | 2016-07-13 | 山东伯仲真空设备股份有限公司 | Special claw type rotor profile |
| CN106949053A (en) * | 2017-05-24 | 2017-07-14 | 中国石油大学(华东) | A kind of claw rotor for including elliptic arc |
| GB2557681A (en) * | 2016-12-15 | 2018-06-27 | Edwards Ltd | A claw pump and method of operation |
| WO2018132019A2 (en) * | 2017-01-10 | 2018-07-19 | John Fleming | Improvements in rotary claw pumps |
| CN111828315A (en) * | 2020-07-24 | 2020-10-27 | 中船重工(重庆)西南装备研究院有限公司 | Double-tooth claw type pump rotor molded line |
| CN113779721A (en) * | 2021-09-08 | 2021-12-10 | 浙江理工大学 | Special claw type vacuum pump molded line design method based on envelope surface correction |
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2021
- 2021-12-30 CN CN202111656647.6A patent/CN114320921B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1676936A (en) * | 2004-03-30 | 2005-10-05 | 肖文伟 | Rotor tooth-profile for screw pump |
| CN105756929A (en) * | 2016-04-22 | 2016-07-13 | 山东伯仲真空设备股份有限公司 | Special claw type rotor profile |
| GB2557681A (en) * | 2016-12-15 | 2018-06-27 | Edwards Ltd | A claw pump and method of operation |
| WO2018132019A2 (en) * | 2017-01-10 | 2018-07-19 | John Fleming | Improvements in rotary claw pumps |
| CN106949053A (en) * | 2017-05-24 | 2017-07-14 | 中国石油大学(华东) | A kind of claw rotor for including elliptic arc |
| CN111828315A (en) * | 2020-07-24 | 2020-10-27 | 中船重工(重庆)西南装备研究院有限公司 | Double-tooth claw type pump rotor molded line |
| CN113779721A (en) * | 2021-09-08 | 2021-12-10 | 浙江理工大学 | Special claw type vacuum pump molded line design method based on envelope surface correction |
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