CN102200114A - Super-efficient single-support compressor having taper hole bearing structure - Google Patents

Super-efficient single-support compressor having taper hole bearing structure Download PDF

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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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compressor
bearing
taper
hole
taper hole
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CN2011101631159A
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Chinese (zh)
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何四发
吴景华
尹小兵
崔磊
杨任平
盛正堂
金文辉
陈永安
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华意压缩机股份有限公司
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Priority to CN2011101631159A priority Critical patent/CN102200114A/en
Publication of CN102200114A publication Critical patent/CN102200114A/en

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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

锥孔轴承结构的超高效单支承压缩机 Single compressor ultra-efficient tapered bore bearing the support structure

技术领域 FIELD

[0001] 本发明涉及压缩机技术领域,具体涉及一种超高效单支承压缩机轴承结构。 [0001] TECHNICAL FIELD The present invention relates in particular to a single ultra-efficient compressor bearing support structure. 背景技术 Background technique

[0002] 压缩机机械磨擦副的磨擦对压缩机的效率有重要的影响,压缩机设计都在尽可能地减少摩擦来提升效率。 [0002] mechanical friction friction pairs compressor has a significant impact on the efficiency of the compressor, the compressor design are to reduce friction as much as possible to improve efficiency. 然而对于超高效单支承压缩机而言,由于曲轴在压缩机连杆力的作用下会发生倾斜,使得曲轴长轴圆柱面和曲轴孔圆柱面在投影方向形成一个夹角即曲轴长轴圆柱面和曲轴孔圆柱面之间形成一个倾斜角,进而使得油压呈单侧分布,这样就会降低压缩机的可靠性和工作效率。 However, for ultra-efficient single support the compressor, since the crankshaft tilts under the action of the compressor rod force, so that the long axis of the crankshaft and the cylindrical surface forming a cylindrical hole circle crankshaft crank angle i.e. the major axis direction cylindrical surface of the projection well round cylindrical form between the crankshaft and a tilt angle, thereby making the hydraulic distribution was unilateral, this will reduce the reliability and efficiency of the compressor. 目前,对于负载相对较小的超高效单支承压缩机,通常只是通过减小曲轴长轴外径来减少纯流体摩擦功率以提升效率,如R600a超高效单支承压缩机的曲轴长轴外径由早期的Φ 16减小到Φ 14,甚至Φ 12,但由于结构设计、润滑、可靠性等多方面原因,很难再通过进一步减小曲轴长轴外径来减少摩擦以提升压缩机效率;而对于负载相对较高的超高效单支承压缩机,减小曲轴长轴外径会带来边缘磨损失效问题,例如将 Currently, the load is relatively small ultra-efficient single support the compressor, but usually the pure fluid friction to reduce power by reducing the outer diameter of the major axis of the crankshaft to improve efficiency, such as R600a single ultra-efficient compressor crankshaft supported by the outer diameter of the major axis early decreased to Φ 16 Φ 14, even Φ 12, but due to various design reasons, lubrication, reliability, very difficult to reduce friction by further reducing the outer diameter of the major axis of the crankshaft in order to enhance the efficiency of the compressor; and for relatively high-load bearing single ultra-efficient compressor, reducing the outer diameter of the major axis of the crankshaft failures lead to edge wear, for example,

超高效单支承压缩机的曲轴长轴外径由Φ16减小到Φ 14时便会出现边缘磨损失效现象,即使是通过增加轴承长度的方式来增加受力面积仍然解决不了边缘磨损失效现象。 Frayed edges will appear a major axis outer diameter of the spent phenomenon of the crankshaft supporting a single ultra-efficient compressor is reduced by a Φ16 to Φ 14, even if the force is increased by increasing the length of the bearing area is still not resolved manner edge wear failure phenomena. 因此,如何在保证超高效单支承压缩机的可靠性前题下进一步提升其工作效率是一道技术难题。 Therefore, how to ensure reliability under the premise supporting ultra-efficient single compressor to further enhance its efficiency is a technical problem.

[0003] 本发明所要解决的技术问题在于怎样进一步地减少磨擦以提升效率,提供一种效率更高的超高效单支承压缩机。 [0003] The present invention solves the technical problem is how to further reduce friction to improve efficiency and provide a more efficient support a single ultra-efficient compressor.

[0004] 为了解决上述技术问题,本发明所采用的解决方案是:一种锥孔轴承结构的超高效单支承压缩机,包括曲轴及曲轴箱,其特征在于:曲轴箱的曲轴孔上端为锥孔。 [0004] To solve the above problems, the solutions of the present invention is employed: single ultra-efficient compressor which support cone bearing structure, comprising a crankshaft and a crankcase, characterized in that: the upper end of the crank hole of the crankcase cone hole. 将曲轴箱的曲轴孔上端设计成锥孔形状,可以改善油压的分布形态从而减少磨擦,在保证超高效单支承压缩机的可靠性前题下进一步提升其工作效率。 The upper end of the crank hole of the crankcase is designed as cone shape can be improved to reduce the distribution form of hydraulic friction, to further enhance its efficiency in ensuring ultra-high reliability of the compressor is supported single premise.

[0005] 根据负载的不同,曲轴箱的曲轴孔可以分成二段,即上端采用锥孔,下端采用圆柱孔或者锥孔,也可以分成三段,即两端为锥孔,中间为圆柱孔;当上端锥孔锥度和下端锥孔锥度与曲轴在连杆力的作用下发生倾斜角度设计成相吻合情况时,使得油压分布由原来的单侧分布转为正态分布,经过加速寿命试验验证表明,此种设计可以有效地解决压缩机在曲轴长轴直径6a由Φ 16减小到Φ 14情况下出现的边缘磨损失效现象,并有效提升了压缩机效率;而对于R600a压缩机,当采用锥孔轴承结构(锥孔小端直径大于或等于圆柱孔直径),由于它的纯流体磨擦功比现有圆柱轴承的纯流体磨擦功要小,亦能有效提升效率。 [0005] can be divided according to different crank hole crankcase Sec load, i.e., an upper tapered bore use, the lower end employs a cylindrical or tapered bore hole, it may be divided into three sections, i.e. two ends of a tapered bore, a cylindrical intermediate hole; when the inclination angle of the upper end of the case is designed to match the taper taper taper taper hole and the lower end of the crankshaft under the action of the force link, so that the hydraulic distribution sided original into normal distribution through accelerated life test verification shows that this design can be effectively solved at the edges in a compressor crankshaft 6a is reduced by the major axis diameter to Φ 16 14 [Phi] where the wear failure phenomena, and effectively improve the efficiency of the compressor; and for R600a compressor, when employed cone bearing structure (small end tapered bore diameter greater than or equal to the cylinder bore diameter), fluid friction due to its pure power than conventional cylindrical bearing pure power fluid friction smaller, are also effective to improve efficiency.

[0006] 本发明由于采用了上述技术方案,它利用锥孔轴承结构使得压缩机产生以下显著效果: [0006] The present invention adopts the above technical solution, which uses a bearing cone structure such that the compressor produces the following remarkable effects:

1、使压缩机的效率提高2.0%以上; 1, so that the efficiency of the compressor is increased by more than 2.0%;

2、对于R600a压缩机,如果上端锥孔锥度和下端锥孔锥度与曲轴在连杆力的作用下发生倾斜的角度设计成相吻合,且在保证可靠性的前提下减短轴承长度,压缩机效率可以提高2. 0%以上,如果不设计成吻合,压缩机可以效率提升1 %以上。 2, a compressor for R600a, if the inclination angle of the tapered upper end and a lower end taper taper taper hole under the action of the crankshaft rod force designed to coincide, and shorten the bearing length to ensure reliability of the premise, the compressor efficiency can be improved by more than 2.0%, if not designed to match the compressor can improve the efficiency of more than 1%. 附图说明 BRIEF DESCRIPTION

[0007] 图1是现有技术中的圆柱轴承工作示意图; 图2是本发明锥孔轴承一种工作情况示意图; 图3是本发明锥孔轴承第一种实施方案; [0007] FIG. 1 is a schematic view of the working cylinder bearing the prior art; FIG. 2 is a schematic view of one of the working cone bearing of the present invention; FIG. 3 is a cone bearing a first embodiment of the present invention embodiment;

图4是本发明锥孔轴承第二种实施方案。 FIG 4 is a tapered bore bearing the second embodiment of the present invention.

具体实施方式 Detailed ways

[0008] 现有技术的情况如图1所示:曲轴1在压缩机连杆力Fl的作用下发生倾斜a°,即曲轴长轴圆柱面Ia和曲轴箱2的曲轴孔圆柱面加,在投影方向的夹角,其中F3 = F1+F2, 其中力F3最大。 Where [0008] the prior art shown in Figure 1: the crank shaft 1 is inclined at a ° compressor rod force Fl effect, i.e., the major axis of the cylindrical surface Ia of the crankshaft and the crankcase crank well round cylinder 2 is added, the the angle between the projection direction, wherein F3 = F1 + F2, where the maximum force F3. 由于倾斜角a°的原因使得油压呈单侧分布,如图1的右侧所示。 The inclination angle a ° of reasons such as a one-sided distribution of hydraulic pressure, shown on the right in FIG. 1.

[0009] 本发明第一种实施方案主要应用于压缩机效率的提升。 [0009] In a first embodiment of the present invention is mainly applied to enhance compressor efficiency. 如图3所示,曲轴箱2的曲轴孔分成三段,即两端为锥孔,中间为圆柱孔,上端锥孔锥度为b°,锥孔长度为b, 锥孔起始内径为Φ13,锥孔末端内径为Ctb + C,中间段为圆柱孔内径为Ctb,圆柱孔长度为h,下端锥孔锥度为C。 3, the crankcase crank hole 2 into three sections, i.e. two ends of a tapered bore, a cylindrical intermediate hole, the upper end of the cone taper b °, cone length is b, the inside diameter of the cone starting Φ13, an inner diameter end of the tapered hole Ctb + C, the middle section is a cylindrical inner hole diameter Ctb, cylindrical hole length is h, the lower end of the cone taper C. ,起始内径为ctb,锥孔末端内径为(tb+ d。上端锥孔锥度b°和下端锥孔锥度C。与曲轴1在连杆力Fl的作用下发生倾斜角度为a°设计成相吻合即曲轴长轴轴承表面la、lb分别与曲轴箱锥孔表面2c、2b在投影方向轮廓线在相应位置平行贴合, 这样使得油压分布由原来的单侧分布转为正态分布,可靠性得到提高,有效的解决了压缩机实现曲轴长轴直径6a由Φ16减小到Φ 14出现的边缘磨损失效现象,并且通过加速寿命试验验证了其正确性,有效了提升了Rl3½压缩机效率。 Starting CTB inner diameter, the inner diameter of the end cone (tb + d. Upper cone and the lower cone taper b ° C. taper inclination angle to the crankshaft 1 occurs at a force of Fl acting link is designed to match a ° i.e., the major axis of the crankshaft bearing surfaces la, lb respectively crankcase cone surface 2c, 2b in a direction of projection parallel to the contour line at a corresponding position bonded, so that the hydraulic distribution sided original into normal distribution reliability improved, effective solution to achieve the compressor 6a of the crankshaft axis diameter Φ16 edge Φ 14 is reduced to wear failure phenomena occur, and verify its validity by the accelerated life test, the effective Rl3½ enhance compressor efficiency.

[0010] 本发明第二种实施方案主要应用于R600a压缩机效率的提升。 [0010] A second embodiment of the present invention is mainly applied to enhance compressor efficiency R600a. 如图4所示,曲轴箱2的曲轴孔分成三段,即两端为锥孔,中间为圆柱孔,上端锥孔锥度为b°,曲轴1的长轴轴承长度b减短到b — K,锥孔起始内径为Φ、锥孔末端内径为(tb + c;中间段为圆柱孔内径为Φ b,圆柱孔长度为h;下端锥孔锥度为C。,曲轴1的长轴轴承长度c减短到cm,起始内径为Φ、锥孔末端内径为(tb+ d。当上端锥孔锥度b°和下端锥孔锥度C°与曲轴1 在连杆力Fl的作用下发生倾斜角度为a°设计成相吻合,油压呈正态分布,曲轴长轴外径为Φβ(目前最小为Φ 12),由于油压呈正态分布使得可靠性提高,这样使得R600a曲轴长轴的轴承长度b和C设计的更小(即b — k和cm),纯流体磨擦功率进一步减少,再加上锥孔轴承速度梯度减少而带来的纯流体磨擦功率减小,使得效率得到提升更加明显。这样解决了R600a压缩机由于多种原因使得曲轴长轴承直径很难再减小的 4, the crankcase crank hole 2 is divided into three sections, i.e. two ends of a tapered bore, a cylindrical intermediate hole, the upper end of the cone taper b [deg.], The length b of the major axis of the crankshaft bearing is shortened to 1 b - K , [Phi] inner diameter of the starting cone, the inner diameter of the end cone (tb + c; for the intermediate section inner diameter of the cylindrical bore Φ b, a length of the cylindrical bore H; lower cone taper C., crankshaft bearing major axis length 1 c shortened to cm, an inner diameter of the starting Φ, an inner diameter of the end cone (tb + d. when the tapered upper end and a lower end taper b ° C ° taper cone tilt angle of the crankshaft under the action of the force Fl is link a ° is designed to coincide, hydraulic normal distribution, a major axis outer diameter of the crankshaft Φβ (current minimum Φ 12), since the normal oil pressure such that the reliability was improved, so that the long axis of the crankshaft bearing length R600a b design smaller and C (i.e., b - k and cm & lt), the pure fluid further reducing the friction power, together with the cone bearing and reduce the velocity gradient caused by the pure fluid friction power is reduced, so that improve efficiency more significantly. this solves a number of reasons R600a compressor crankshaft so that the long diameter of the bearing is hard to decrease 况下,实现了压缩机效率的再次提升。对于R600a的压缩机由于其负载远远小于压缩机,在目前使用的曲轴上不存在边缘磨损的问题,设计锥孔轴承时,上端锥孔锥度b°和下端锥孔锥度C。与曲轴1在连杆力Fl的作用下发生倾斜角度为a°可以设计成相吻合,也可以设计成不相吻合, 都能减少磨擦,这主要是由于采用锥孔轴承后其锥孔端流体的速度梯度比圆柱轴承相应位置流体的速度梯度更小(圆柱孔内径为Φ、圆锥孔起始内径为Φ、终止内径为(tb+ c,这样圆锥孔与曲轴长轴之间是一个变间隙且其间隙均大于原来的圆柱孔即图1中的Φ、虽然单纯的增加圆柱孔的内径可以减少润滑油的速度梯度,但会整体增加曲轴长轴与曲轴箱曲轴孔间隙,由于目前曲轴采用的是螺旋油槽上油,这样会降低曲轴润滑油的上油高度影响润滑,而锥孔轴承是利用锥孔这一特定形状 Under conditions, to achieve once again raise the efficiency of the compressor for R600a compressor load due to its much smaller than the compressor, edge wear is not currently used on the crankshaft problem, when designing bearing cone, tapered upper taper b ° C. and lower cone taper inclination angle to the crankshaft 1 occurs in the rod force Fl role may be designed as a ° coincide, it can also be designed so as not to coincide, can reduce friction, primarily due to the use of cone after the bore bearings speed cone end of the fluid gradient than cylindrical bearing the respective position of the fluid velocity gradient is smaller (cylinder bore inner diameter Φ, conical bore starting inner diameter of Φ, terminating inside diameter (tb + c, so that the conical bore with the crank length and a variable gap is greater than the gap that is the original cylindrical bore in FIG. 1 Φ, although simply increasing the inner diameter of the cylindrical bore can be reduced velocity gradient between the shaft of the lubricating oil, but an overall increase in the long axis of the crankshaft and a crankcase crankshaft clearance hole, due to the current crankshaft oil is used in a helical oil groove, this will reduce the high impact oil lubricant lubricating the crankshaft, and a bearing using tapered bore tapered bore of the particular shape 以递增的方式增加间隙,这样上油孔的位置就可以设计在锥孔的下端面,从而解决因间隙增加过大带来的上油问题,使纯流体磨擦功率下降,提升效率。但是如果上端锥孔锥度b°和下端锥孔锥度C°与曲轴1在连杆力Fl 的作用下发生倾斜角度a°不设计成相吻合,其油压仍然是单侧分布,可靠性就不会得到提高,这样R600a曲轴长轴的轴承长度b和C就很难设计得更短,其效率提高仅仅是由于锥孔轴承速度梯度减少来实现。 Incrementally increase the gap, so that the hole position can be designed in a tapered hole end surface, so as to solve problems due to increased gap is too large to bring the oil, so that the pure fluid friction power down, to improve efficiency, but if the upper end taper of hole inclination angle b ° and a ° is not designed to match the taper cone C ° lower end of the crankshaft 1 occurs in the link action force Fl, which is still one-sided distribution of hydraulic pressure, will not get improved reliability such R600a crankshaft bearing length b of the major axis and the shorter C it is difficult to design, because its efficiency is only reduced tapered bore bearings velocity gradient is achieved.

Claims (5)

1. 一种锥孔轴承结构的超高效单支承压缩机,包括曲轴及曲轴箱,其特征在于:曲轴箱的曲轴孔上端形状为锥孔。 A single ultra-efficient compressor tapered bore bearing the support structure, includes a crankshaft and a crankcase, wherein: the shape of the upper end of the crank hole of the crankcase cone.
2.根据权利要求1所述锥孔轴承结构的超高效单支承压缩机,其特征在于:曲轴箱的曲轴孔由上端的锥孔和下端的圆柱孔组成。 1 according to the single ultra-efficient compressor bearing cone bearing structure according to claim, wherein: the crank hole of the crankcase and the cylinder bore by the tapered bore of the upper end of the lower end of the composition.
3.根据权利要求1所述锥孔轴承结构的超高效单支承压缩机,其特征在于:曲轴箱的曲轴孔由上端的锥孔和下端的锥孔组成。 3. The method of claim 1 bearing a single ultra-efficient compressor tapered bore of the bearing structure, characterized in that: the crankcase crank hole taper hole and the taper hole of the upper end of the lower end of the composition.
4.根据权利要求1所述锥孔轴承结构的超高效单支承压缩机,其特征在于:曲轴箱的曲轴孔由上端的锥孔和下端的锥孔以及中间段的圆柱孔组成。 1 according to the single ultra-efficient compressor bearing cone bearing structure according to claim, wherein: the crankcase crank hole taper hole and the taper hole, and the lower end of the cylindrical bore of the intermediate section of the upper end of the composition.
5.根据权利要求1或2或3或4所述锥孔轴承结构的超高效单支承压缩机,其特征在于:锥孔的锥度与曲轴在连杆力的作用下发生倾斜的角度吻合。 According to claim 1 or 2 or 34 or a single ultra-efficient compressor bearing cone bearing structure according to claim, wherein: consistent taper angle of inclination of the crankshaft the taper hole under the action of force link.
CN2011101631159A 2011-06-17 2011-06-17 Super-efficient single-support compressor having taper hole bearing structure CN102200114A (en)

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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

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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 (5)

* Cited by examiner, † Cited by third party
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
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
CN106246508B (en) * 2016-09-06 2018-09-18 珠海凌达压缩机有限公司 Compressor

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