CN103629115A - Inclined blade groove structure of rolling rotor compressor - Google Patents
Inclined blade groove structure of rolling rotor compressor Download PDFInfo
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- CN103629115A CN103629115A CN201210299338.2A CN201210299338A CN103629115A CN 103629115 A CN103629115 A CN 103629115A CN 201210299338 A CN201210299338 A CN 201210299338A CN 103629115 A CN103629115 A CN 103629115A
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Abstract
The invention provides an inclined blade groove structure of a rolling rotor compressor. The compressor comprises a cylinder, a piston, a crankshaft and a blade. The cylinder is provided with a blade groove and a guide seat. The blade groove which is inclined relative to the center line of a conventional blade groove is formed by anticlockwise rotating the conventional blade groove by a certain angle with the intersection point of the internal diameter of the cylinder and the center line of the conventional blade groove passing through the center of the cylinder on the inner wall of the cylinder as a center, wherein the angle of inclination Psi is greater than 0 DEG and less than 22 DEG. The inclined blade groove structure is an asymmetric blade movement structure directed at asymmetric load of a traditional compressor running in an angle range of 0 to 360 DEG, can greatly reduce a contact force between the blade and the blade groove in the cylinder and the tip of the piston, so friction loss of the blade groove, the tip of the blade and an eccentric part is reduced, and the efficiency of the compressor is improved; moreover, stress on the blade is improved. When the inclined blade groove structure is used on a rotary compressor, input power of the rotary compressor is maximumly decreased by 1.0%, efficiency of the rotary compressor is substantially improved, bearing reaction at the side surface of the blade is maximumly decreased by 17%, and reduction of wearing of the blade and the blade groove enables operational reliability to be improved.
Description
Technical field
The present invention relates to a kind of rolling rotor type compressor, particularly relate to a kind of blade groove structure of rolling rotor type compressor.
Background technique
For rolling rotor type compressor, when operation, its mechanical friction loss accounts for 30% ~ 40% of compressor overall power loss, the frictional loss wherein being caused by blade groove, blade tip and eccentric part accounts for the more than 60% of total mechanical friction loss, reducing the frictional loss at these several places, is the important channel of improving compressor efficiency.Blade and blade groove, because stress condition is severe, are also one of regions the most easily occurring functional reliability problem simultaneously.
Traditional rolling rotor type compressor cylinder blade groove (also referred to as former blade groove) center line AA ' process cylinder axis O, as shown in Figure 1.When the eccentric part that piston 20 is followed bent axle 30 in cylinder 10 is done eccentric circular movement, blade 40 slides and fits tightly with piston 20 in blade groove 101, and motion mode is periodically to-and-fro motion.When piston 20 runnings are defined as 0 ° when extremely the top, blade 40 are in upper dead center, compressor rotates and within one week, is 360 °.
Generally, for reducing the above frictional loss everywhere of conventional construction, main method is to improve machining accuracy, carry out sliding degree and wear resistance that surface treatment etc. increases them, but actual effect not obvious.According to finding the research of compressor load characteristic, in 0 ~ 360 ° of whole compressor operation, load is seriously asymmetric.Front half period (0 ~ 180 °) load is minimum, and (180 ~ 360 °) load of later half cycle is along with the pressure in compression chamber raises and sharply rises and reach maximum value when exhaust just starts.This asymmetric load character has determined that symmetrical conventional construction does not reach optimum in design.Therefore, how from the source of structural design, reducing blade groove frictional loss, the frictional loss of blade tip and eccentric part frictional loss is to be worth very much research and problem urgently to be resolved hurrily.
Summary of the invention
The object of the invention is to provide a kind of rolling rotor type compressor with oblique installing type blade groove structure for overcoming the structural deficiency of above existing rolling rotor type compressor blade groove.
Realizing above-mentioned purpose technological scheme is: a kind of rolling rotor type compressor oblique installing type blade groove structure is provided, a kind of rolling rotor type compressor oblique installing type blade groove structure, described rolling rotor type compressor comprises cylinder, piston, bent axle, blade, wherein, blade groove and the coupled logical guide holder with cylindrical bore that cylinder is provided with that blade can slide in groove and fits tightly with piston, wherein, described blade groove is through the center line of cylinder axis, centered by the intersection point on cylinder inner wall, to rotate counterclockwise an angle by cylinder bore diameter and former blade groove, form the blade groove that a center line with respect to former blade groove tilts, its tilt angle is Ψ, Ψ is greater than 0 ° and is less than 22 °.
Rolling rotor type compressor oblique installing type blade groove structure as previously discussed, wherein, described tilt angle Ψ is 5 ~ 15 °.
Therefore, the present invention adopts oblique installing type blade groove structure, it is the set asymmetric blade movement structure of asymmtric load turning round in 0 ~ 360 ° for traditional compressor, can larger reduction blade and the contact force of cylinder blade groove and piston tip, thereby reduce blade groove frictional loss, the frictional loss of blade tip and eccentric part frictional loss, promote compressor efficiency; Improve vane stress simultaneously, improved compressor reliability.The present invention is that after using on the rotary frequency-changeable compressor of 2, the input power decline maximum of compressor reaches 1.0% at the power of our company exploitation, and compressor efficiency obviously promotes; It is maximum 17% that blade side support reaction declines, and the possibility of blade and blade groove wearing and tearing reduces, and its functional reliability is improved.
Accompanying drawing explanation
Fig. 1 is traditional rolling rotor type compressor cylinder blade groove structural representation;
Fig. 2 is the schematic diagram of rolling rotor type compressor oblique installing type blade groove structure of the present invention;
Fig. 3 is the force analysis figure of traditional rolling rotor type compressor cylinder blade groove structure;
Fig. 4 is the force analysis figure of rolling rotor type compressor oblique installing type blade groove structure of the present invention.
Embodiment
Refer to Fig. 2, rolling rotor type compressor oblique installing type blade groove structure comprises cylinder 1, piston 2, bent axle 3, blade 4, wherein, and blade groove 11 and coupled logical guide holder 12 that cylinder 1 is provided with that blade 4 can slide in groove and fits tightly with piston 2.Described blade groove rotates counterclockwise an angle through the center line AA of cylinder axis O centered by the intersection point G on cylinder inner wall by cylinder bore diameter and former blade groove, form one with respect to former blade groove center line AA blade groove 11 inclination, that namely center line is BB, tilt angle is Ψ, and Ψ is not more than 22 °.Better, tilt angle Ψ is at 5 ~ 15 °.Guide holder 12 is positioned at above blade groove 11 with being connected.And comprise the spring being arranged in its cylindrical bore, position change due to blade groove 11, the position of corresponding guide holder 23 also changes thereupon, on the line stretcher of its cylindrical bore center (plane showing with Fig. 2) in blade groove 11 center line BB, or the line stretcher of its cylindrical bore center line and blade groove 11 center line BB intersects also perpendicular.
Refer to Fig. 3 and Fig. 4, take traditional rolling rotor type compressor blade groove structure and blade groove structure of the present invention separately force-bearing situation make Performance Ratio as example.The center line AA of tradition rolling rotor type compressor cylinder blade groove 101 structures is through cylinder axis O, when the eccentric part of bent axle 30 runs to the angle approaching shown in Fig. 3, the suffered load of blade 40 reaches peak value, is now applied to Main Function power on blade 40 as shown in Figure 3.Wherein Fbr is making a concerted effort of blade X-direction gas force, spring force and inertial force, and Fvv is vane-piston contact force, and R1 is blade front end support reaction, and R2 is blade tail end support reaction.In X-direction, X-direction component F vv*cos Ψ and the Fbr of Fvv are a pair of equilibrant.
In the present invention, adopt blade groove 11 inclined structures to change the contact force direction of blade 4 with piston 2, the angle Ψ of Fvv and X-direction is diminished, cos Ψ increases.In order to make still to meet in X-direction the condition of equilibrant, Fvv will inevitably reduce, and adopts oblique installing type blade groove 11 rear blades 4 will reduce with piston contact force, as shown in Figure 4.
Meanwhile, in the Y direction, R1, R2, Fvv*sin Ψ and blade Y-direction gas force form mechanical equilibrium, after the contact force Fvv of blade 4 and piston 2 reduces, as by power R1, R2 in order to make blade still maintain mechanical equilibrium in Y-direction, will synchronously reduce.
Synthetically see and adopt oblique installing type blade groove 11, not only can reduce the contact force Fvv of blade 4 and piston 2, can also reduce support reaction R1, the R2 of blade 4, this not only can reduce mechanical friction loss, improve compressor efficiency, but also can improve the reliability of compressor.
In addition,, for whole mechanical loss is declined significantly, suitable blade lean angle need to be set, for the compressor of different model, this tilt angle Ψ, is generally Ψ and is greater than 0 ° and is less than 22 °, for example, in the time of 0.1 °, blade 4 is larger with the contact force of piston 2, and its wearing and tearing start to reduce, but limited, power declines few, and in the time of 22 °, blade 4 no longer reduces with the contact force of piston 2, wearing and tearing also no longer reduce, so the not obvious increase of the very little compressor efficiency of power fall.Better being positioned between 5 ° ~ 15 °, now, as the input power of above-mentioned rotary frequency-changeable compressor has declined 0.5 ~ 1.0%, compressor efficiency obviously promotes; It is maximum 12 ~ 17% that blade side support reaction declines, and blade and blade groove wearing and tearing obviously reduce, and the reliability of use improves, and is in the best situation of combination property.
Claims (3)
1. a rolling rotor type compressor oblique installing type blade groove structure, rolling rotor type compressor comprises cylinder, piston, bent axle, blade, wherein, blade groove and the coupled logical guide holder with cylindrical bore that cylinder is provided with that blade can slide in groove and fits tightly with piston, it is characterized in that, described blade groove is through the center line of cylinder axis, centered by the intersection point on cylinder inner wall, to rotate counterclockwise an angle by cylinder bore diameter and former blade groove, form the blade groove that a center line with respect to former blade groove tilts, its tilt angle is Ψ, Ψ is greater than 0 ° and is less than 22 °.
2. rolling rotor type compressor oblique installing type blade groove structure as claimed in claim 1, is characterized in that, described tilt angle Ψ is 5 ~ 15 °.
3. rolling rotor type compressor oblique installing type blade groove structure as claimed in claim 1 or 2, is characterized in that, on the line stretcher of the cylindrical inner circle center of described guide holder in blade groove center line.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210299338.2A CN103629115B (en) | 2012-08-22 | 2012-08-22 | Rolling rotor compressor inclined type blade groove structure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210299338.2A CN103629115B (en) | 2012-08-22 | 2012-08-22 | Rolling rotor compressor inclined type blade groove structure |
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| CN103629115A true CN103629115A (en) | 2014-03-12 |
| CN103629115B CN103629115B (en) | 2016-09-28 |
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| CN201210299338.2A Active CN103629115B (en) | 2012-08-22 | 2012-08-22 | Rolling rotor compressor inclined type blade groove structure |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106768566A (en) * | 2017-03-15 | 2017-05-31 | 广西大学 | A kind of friction measurement device of rolling piston compressor slide plate and chute |
| CN108603505A (en) * | 2016-02-15 | 2018-09-28 | 三菱电机株式会社 | Rotary compressor |
| CN112576504A (en) * | 2020-12-14 | 2021-03-30 | 周村华祥机械加工厂 | Inflator device |
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| JPH0849675A (en) * | 1994-08-04 | 1996-02-20 | Hitachi Ltd | Rotary compressor |
| CN101187373A (en) * | 2006-11-20 | 2008-05-28 | Lg电子株式会社 | Variable capacity type rotary compressor |
| CN101684812A (en) * | 2008-09-25 | 2010-03-31 | 三星电子株式会社 | Cylinder for rotary compressor and rotary compressor having the same |
| CN101769166A (en) * | 2008-12-30 | 2010-07-07 | 上海日立电器有限公司 | Two-stage rolling rotor-type expander |
| CN102216618A (en) * | 2008-11-19 | 2011-10-12 | 康奈可关精株式会社 | Gas compressor |
| CN102330685A (en) * | 2010-07-12 | 2012-01-25 | 三菱电机株式会社 | Vane compressor |
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2012
- 2012-08-22 CN CN201210299338.2A patent/CN103629115B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0849675A (en) * | 1994-08-04 | 1996-02-20 | Hitachi Ltd | Rotary compressor |
| CN101187373A (en) * | 2006-11-20 | 2008-05-28 | Lg电子株式会社 | Variable capacity type rotary compressor |
| CN101684812A (en) * | 2008-09-25 | 2010-03-31 | 三星电子株式会社 | Cylinder for rotary compressor and rotary compressor having the same |
| CN102216618A (en) * | 2008-11-19 | 2011-10-12 | 康奈可关精株式会社 | Gas compressor |
| CN101769166A (en) * | 2008-12-30 | 2010-07-07 | 上海日立电器有限公司 | Two-stage rolling rotor-type expander |
| CN102330685A (en) * | 2010-07-12 | 2012-01-25 | 三菱电机株式会社 | Vane compressor |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108603505A (en) * | 2016-02-15 | 2018-09-28 | 三菱电机株式会社 | Rotary compressor |
| CN106768566A (en) * | 2017-03-15 | 2017-05-31 | 广西大学 | A kind of friction measurement device of rolling piston compressor slide plate and chute |
| CN106768566B (en) * | 2017-03-15 | 2023-05-05 | 广西大学 | Friction force measuring device for sliding vane and sliding chute of rolling piston compressor |
| CN112576504A (en) * | 2020-12-14 | 2021-03-30 | 周村华祥机械加工厂 | Inflator device |
| CN112576504B (en) * | 2020-12-14 | 2024-03-15 | 步跃医疗器械(淄博)有限公司 | Inflator device |
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| CN103629115B (en) | 2016-09-28 |
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Address after: 201206 Jinqiao Road, Pudong New Area Jinqiao Export Processing Zone, Shanghai, 1051 Patentee after: Shanghai Haili Electrical Appliance Co. Ltd. Address before: 201206 Jinqiao Road, Pudong New Area Jinqiao Export Processing Zone, Shanghai, 1051 Patentee before: Rili Electric Appliance Co., Ltd., Shanghai |
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