CN102200114A - Super-efficient single-support compressor having taper hole bearing structure - Google Patents
Super-efficient single-support compressor having taper hole bearing structure Download PDFInfo
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- CN102200114A CN102200114A CN2011101631159A CN201110163115A CN102200114A CN 102200114 A CN102200114 A CN 102200114A CN 2011101631159 A CN2011101631159 A CN 2011101631159A CN 201110163115 A CN201110163115 A CN 201110163115A CN 102200114 A CN102200114 A CN 102200114A
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- bent axle
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Abstract
The invention provides a super-efficient single-support compressor having a taper hole bearing structure. A crank shaft hole of a crank case is designed to be a taper hole to further reduce the friction between a long axis of a crank shaft and a bearing and improve the reliability and the efficiency of the compressor. By the invention, the efficiency of the compressor R134a can be improved by over 2.0 percent. For the compressor R600a, if the taper of an upper-end taper hole, the taper of a lower-end taper hole and the inclined angle of the crank shaft are matched, the efficiency of the compressor can be improved by over 2.0 percent by shortening the length of the bearing on the premise of ensuring the reliability, and the efficiency of the compressor can be improved by over 1.0 percent if the taper of the upper-end taper hole, the taper of the lower-end taper hole and the inclined angle of the crank shaft are not matched.
Description
Technical field
The present invention relates to the Compressor Technology field, be specifically related to the single supporting of a kind of ultra high efficiency compressor shaft bearing structure.
Background technique
The friction of compressor mechanical friction pair has significant effects to the efficient of compressor, and compressor design is all reduced friction as much as possible and promoted efficient.Yet for the single supporting of ultra high efficiency compressor, because bent axle is the meeting run-off the straight under the effect of compressor connecting bar power, make that bent axle major axis cylndrical surface and crankshaft hole cylndrical surface are to form a tilt angle between bent axle major axis cylndrical surface and the crankshaft hole cylndrical surface projecting direction shape in an angle, and then make oil pressure be one-sided distribution, will reduce the reliability and the working efficiency of compressor like this.At present, for the less relatively single supporting of the ultra high efficiency compressor of load, usually just reduce pure fluid friction power to promote efficient by reducing bent axle major axis external diameter, bent axle major axis external diameter as the single supporting of R600a ultra high efficiency compressor is reduced to φ 14 by early stage φ 16, even φ 12, but, be difficult to reduce friction to promote compressor efficiency by further reducing bent axle major axis external diameter again owing to many-sided reasons such as structural design, lubricated, reliabilities; And for the higher relatively single supporting of the ultra high efficiency compressor of load, reduce bent axle major axis external diameter and can bring the edge abrasion Problem of Failure, just the edge abrasion failure phenomenon can occur when for example the single bent axle major axis external diameter that supports compressor of R134a ultra high efficiency being reduced to φ 14 by φ 16, still can't resolve the edge abrasion failure phenomenon even increase lifting surface area by the mode that increases bearing length.Therefore, how further promoting its working efficiency under the topic before the reliability that guarantees the single supporting of ultra high efficiency compressor is one technical barrier.
Technical problem to be solved by this invention is to reduce friction how further to promote efficient, and the single supporting of the higher ultra high efficiency of a kind of efficient compressor is provided.
In order to solve the problems of the technologies described above, solution of the present invention is: the single supporting of a kind of ultra high efficiency of tapered bore bearing structure compressor, comprise bent axle and crankcase, and it is characterized in that: the crankshaft hole upper end of crankcase is taper hole.The crankshaft hole upper end of crankcase is designed to the taper hole shape, thereby the distributional pattern that can improve oil pressure reduces friction, before the reliability that guarantees the single supporting of ultra high efficiency compressor, further promote its working efficiency under the topic.
According to the difference of load, the crankshaft hole of crankcase can be divided into two sections, and promptly taper hole is adopted in the upper end, and cylindrical hole or taper hole are adopted in the lower end, also can be divided into three sections, and promptly two ends are taper hole, and the centre is a cylindrical hole; When upper end taper hole tapering and lower end taper hole tapering and bent axle the angle of inclination take place when being designed to match situation under the effect of connecting rod power, make oil pressure distribute and transfer normal distribution to by original one-sided distribution, show through the accelerated life test checking, this kind design can solve the R134a compressor effectively and is reduced to the edge abrasion failure phenomenon that occurs under φ 14 situations by φ 16 at bent axle major diameter φ a, and has effectively promoted the R134a compressor efficiency; And,,, also can effectively promote efficient because its pure fluid friction merit is littler than the pure fluid friction merit of existing cylindrical bearing when adopting tapered bore bearing structure (the taper hole end diameter is more than or equal to the cylindrical hole diameter) for the R600a compressor.
The present invention is owing to adopted technique scheme, and it utilizes the tapered bore bearing structure to make compressor produce following remarkable result:
1, make the efficient of R134a compressor improve more than 2.0%;
2, for the R600a compressor, if upper end taper hole tapering becomes to match with the angle design of lower end taper hole tapering with bent axle run-off the straight under the effect of connecting rod power, and under the prerequisite that guarantees reliability, shorten bearing length, compressor efficiency can improve more than 2.0%, if be not designed to coincide, compressor can efficiengy-increasing more than 1%.
Description of drawings
Fig. 1 is a cylindrical bearing work schematic representation of the prior art;
Fig. 2 is a kind of working condition schematic representation of tapered bore bearing of the present invention;
Fig. 3 is first kind of embodiment of tapered bore bearing of the present invention;
Fig. 4 is second kind of embodiment of tapered bore bearing of the present invention.
Embodiment
The situation of prior art is as shown in Figure 1: bent axle 1 under the effect of compressor connecting bar power F1 run-off the straight a °, i.e. and the crankshaft hole cylndrical surface 2a of bent axle major axis cylndrical surface 1a and crankcase 2, at the angle of projecting direction, wherein F3=F1+F2, wherein power F3 maximum.Owing to tilt angle a ° reason makes oil pressure be one-sided distribution, shown in the right side of Fig. 1.
First kind of embodiment of the present invention is mainly used in the lifting of R134a compressor efficiency.As shown in Figure 3, the crankshaft hole of crankcase 2 is divided into three sections, and promptly two ends are taper hole, the centre is a cylindrical hole, upper end taper hole tapering is b °, and taper hole length is b, and the initial internal diameter of taper hole is φ b, the terminal internal diameter of taper hole is φ b+c, intermediate section is φ b for the cylindrical hole internal diameter, and cylindrical hole length is h, and lower end taper hole tapering is C °, initial internal diameter is φ b, and the terminal internal diameter of taper hole is φ b+d.The angle of inclination takes place and is a ° to be designed to match be bent axle major axis bearing surface 1a in C ° of b ° of upper end taper hole tapering and lower end taper hole tapering and bent axle 1 under the effect of connecting rod power F1,1b respectively with crankcase taper hole surface 2c, 2b is in the parallel applying in the relevant position of projecting direction profile line, make oil pressure distribute like this and transfer normal distribution to by original one-sided distribution, reliability is improved, effectively solved the R134a compressor and realized that bent axle major diameter φ a is reduced to the edge abrasion failure phenomenon that φ 14 occurs by φ 16, and verified its correctness by accelerated life test, effective R134a compressor efficiency that promoted.
Second kind of embodiment of the present invention is mainly used in the lifting of R600a compressor efficiency.As shown in Figure 4, the crankshaft hole of crankcase 2 is divided into three sections, and promptly two ends are taper hole, and the centre is a cylindrical hole, and upper end taper hole tapering is b °, and the major axis bearing length b of bent axle 1 shortens b-K, and the initial internal diameter of taper hole is φ b, and the terminal internal diameter of taper hole is φ b+c; Intermediate section is φ b for the cylindrical hole internal diameter, and cylindrical hole length is h; Lower end taper hole tapering is C °, and the major axis bearing length c of bent axle 1 shortens c-m, and initial internal diameter is φ b, and the terminal internal diameter of taper hole is φ b+d.Be a ° and be designed to match when the angle of inclination takes place under the effect of connecting rod power F1 for C ° of b ° of upper end taper hole tapering and lower end taper hole tapering and bent axle 1, oil pressure is normal distribution, bent axle major axis external diameter is the minimum at present φ 12 of being of φ a(), because being normal distribution, oil pressure make reliability improve, littler (being b-k and c-m) that makes the bearing length b of R600a bent axle major axis and C design like this, pure fluid friction power further reduces, the pure fluid friction power reduction of adding the minimizing of tapered bore bearing velocity gradient and bringing, it is more obvious to make efficient get a promotion.Solved the R600a compressor like this and realized the lifting once more of compressor efficiency under the situation that bent axle long bearing diameter is difficult to reduce again owing to multiple reason makes.Compressor for R600a is far smaller than the R134a compressor owing to its load, the problem that on the bent axle that uses at present, does not have edge abrasion, during the design tapered bore bearing, the angle of inclination takes place and is a ° and can be designed to match in C ° of b ° of upper end taper hole tapering and lower end taper hole tapering and bent axle 1 under the effect of connecting rod power F1, also can be designed to not match, can both reduce friction, this mainly is that littler (the cylindrical hole internal diameter is φ b because the velocity gradient that adopts its taper hole end fluid behind the tapered bore bearing is than the velocity gradient of cylindrical bearing relevant position fluid, the initial internal diameter of conical bore is φ b, stopping internal diameter is φ b+c, between conical bore and the bent axle major axis being one like this, to become gap and its gap be φ b among Fig. 1 greater than original cylindrical hole all, though the internal diameter of simple increase cylindrical hole can reduce the velocity gradient of lubricant oil, but can wholely increase bent axle major axis and crankcase crankshaft hole gap, because what bent axle adopted at present is that helical oil groove oils, the effect of altitude that oils that can reduce crank lubricating like this is lubricated, and tapered bore bearing is to utilize this given shape of taper hole to increase the gap in the mode that increases progressively, the lower end surface at taper hole just can be designed in the position of upper oil hole like this, thereby solve because of the excessive problem of bringing that oils of gap increase, pure fluid friction power is descended, promote efficient.If be not designed to match but b ° of upper end taper hole tapering and lower end taper hole tapering take place angle of inclination a ° with bent axle 1 for C ° under the effect of connecting rod power F1, its oil pressure remains one-sided distribution, reliability just can not be improved, the bearing length b of R600a bent axle major axis and C just are difficult to design shortlyer like this, and it only is because the tapered bore bearing velocity gradient reduces and realizes that its efficient improves.
Claims (5)
1. the single supporting of the ultra high efficiency of tapered bore bearing structure compressor comprises bent axle and crankcase, it is characterized in that: the crankshaft hole upper end of crankcase is shaped as taper hole.
2. according to the single supporting of the ultra high efficiency compressor of the described tapered bore bearing structure of claim 1, it is characterized in that: the crankshaft hole of crankcase is made up of the taper hole of upper end and the cylindrical hole of lower end.
3. according to the single supporting of the ultra high efficiency compressor of the described tapered bore bearing structure of claim 1, it is characterized in that: the crankshaft hole of crankcase is made up of the taper hole of upper end and the taper hole of lower end.
4. according to the single supporting of the ultra high efficiency of the described tapered bore bearing structure of claim 1 compressor, it is characterized in that: the crankshaft hole of crankcase is made up of the taper hole of upper end and the taper hole of lower end and the cylindrical hole of intermediate section.
5. according to the single supporting of the ultra high efficiency compressor of claim 1 or 2 or 3 or 4 described tapered bore bearing structures, it is characterized in that: the angle of the tapering of taper hole and bent axle run-off the straight under the effect of connecting rod power is coincide.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011101631159A CN102200114A (en) | 2011-06-17 | 2011-06-17 | Super-efficient single-support compressor having taper hole bearing structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011101631159A CN102200114A (en) | 2011-06-17 | 2011-06-17 | Super-efficient single-support compressor having taper hole bearing structure |
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| CN102200114A true CN102200114A (en) | 2011-09-28 |
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| CN2011101631159A Pending CN102200114A (en) | 2011-06-17 | 2011-06-17 | Super-efficient single-support compressor having taper hole bearing structure |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105715511A (en) * | 2014-12-18 | 2016-06-29 | Lg电子株式会社 | Compressor |
| CN106246508A (en) * | 2016-09-06 | 2016-12-21 | 珠海凌达压缩机有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
| CN107131109A (en) * | 2016-02-29 | 2017-09-05 | 日立空调·家用电器株式会社 | Compressor and the refrigerator for possessing the compressor |
| JPWO2020095903A1 (en) * | 2018-11-08 | 2021-09-02 | パナソニック株式会社 | Refrigerant compressor and refrigeration equipment using it |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1193695A (en) * | 1996-06-17 | 1998-09-23 | 株式会社丰田自动织机制作所 | Variable displacement compressor |
| US20070017318A1 (en) * | 2005-07-19 | 2007-01-25 | Bear Corporation | Wedging bicycle crank |
| CN101798967A (en) * | 2009-02-10 | 2010-08-11 | 重庆动源摩托车配件销售有限公司 | Engine for motorcycle |
| CN202073746U (en) * | 2011-06-17 | 2011-12-14 | 华意压缩机股份有限公司 | Ultrahigh-efficiency single-support compressor with tapered bore bearing structure |
-
2011
- 2011-06-17 CN CN2011101631159A patent/CN102200114A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1193695A (en) * | 1996-06-17 | 1998-09-23 | 株式会社丰田自动织机制作所 | Variable displacement compressor |
| US20070017318A1 (en) * | 2005-07-19 | 2007-01-25 | Bear Corporation | Wedging bicycle crank |
| CN101798967A (en) * | 2009-02-10 | 2010-08-11 | 重庆动源摩托车配件销售有限公司 | Engine for motorcycle |
| CN202073746U (en) * | 2011-06-17 | 2011-12-14 | 华意压缩机股份有限公司 | Ultrahigh-efficiency single-support compressor with tapered bore bearing structure |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105715511A (en) * | 2014-12-18 | 2016-06-29 | Lg电子株式会社 | Compressor |
| CN105715511B (en) * | 2014-12-18 | 2018-03-23 | Lg电子株式会社 | Compressor |
| US10859076B2 (en) | 2014-12-18 | 2020-12-08 | Lg Electronics Inc. | Compressor |
| CN107131109A (en) * | 2016-02-29 | 2017-09-05 | 日立空调·家用电器株式会社 | Compressor and the refrigerator for possessing the compressor |
| CN106246508A (en) * | 2016-09-06 | 2016-12-21 | 珠海凌达压缩机有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
| CN106246508B (en) * | 2016-09-06 | 2018-09-18 | 珠海凌达压缩机有限公司 | Compressor with a compressor housing having a plurality of compressor blades |
| JPWO2020095903A1 (en) * | 2018-11-08 | 2021-09-02 | パナソニック株式会社 | Refrigerant compressor and refrigeration equipment using it |
| JP7142100B2 (en) | 2018-11-08 | 2022-09-26 | パナソニックホールディングス株式会社 | Refrigerant compressor and refrigeration system using the same |
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Application publication date: 20110928 |