WO2016197373A1 - 用于回转式压缩机的曲轴和具有其的回转式压缩机 - Google Patents

用于回转式压缩机的曲轴和具有其的回转式压缩机 Download PDF

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Publication number
WO2016197373A1
WO2016197373A1 PCT/CN2015/081266 CN2015081266W WO2016197373A1 WO 2016197373 A1 WO2016197373 A1 WO 2016197373A1 CN 2015081266 W CN2015081266 W CN 2015081266W WO 2016197373 A1 WO2016197373 A1 WO 2016197373A1
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WO
WIPO (PCT)
Prior art keywords
eccentric portion
rotary compressor
crankshaft
projection point
central axis
Prior art date
Application number
PCT/CN2015/081266
Other languages
English (en)
French (fr)
Inventor
周杏标
汤昕鑫
Original Assignee
广东美芝制冷设备有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 广东美芝制冷设备有限公司 filed Critical 广东美芝制冷设备有限公司
Priority to JP2017533672A priority Critical patent/JP6398012B2/ja
Priority to US15/502,208 priority patent/US10260504B2/en
Priority to EP15894643.4A priority patent/EP3309400B1/en
Priority to PCT/CN2015/081266 priority patent/WO2016197373A1/zh
Publication of WO2016197373A1 publication Critical patent/WO2016197373A1/zh

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Classifications

    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/18—Eccentric-shafts
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • the present invention relates to the field of compressors, and more particularly to a crankshaft for a rotary compressor and a rotary compressor having the same.
  • the related art indicates that the eccentric portion of the rotary compressor is cylindrical, the piston sleeve is disposed on the outer peripheral surface of the eccentric portion, and the entire inner circumferential surface of the piston is in contact with the entire outer circumferential surface of the eccentric portion.
  • the eccentric portion drives the piston to rotate, there is friction loss, so the eccentric portion is provided with an oil hole to improve the lubrication between the eccentric portion and the piston.
  • the piston is subjected to high and low differential pressure gas forces and is transmitted to the eccentric portion through the oil film between the piston and the eccentric portion. Because the bearing area of the outer peripheral surface of the eccentric portion is different in different regions, the position of the oil hole affects the oil film distribution and even destroys the bearing of the oil film, resulting in abnormal wear. In addition, since the eccentric portion causes the frictional loss when the piston rotates, the working load of the rotary compressor is increased.
  • the present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention is required to provide a crankshaft for a rotary compressor that has a long service life.
  • the present invention also needs to provide a rotary compressor having the above crankshaft.
  • a crankshaft for a rotary compressor includes: a body having an oil supply passage formed therein; and an eccentric portion, the eccentric portion being sleeved on the body,
  • the central axis of the eccentric portion is eccentrically disposed with respect to a central axis of the body, and the eccentric portion is formed with an oil outlet hole communicating with the oil supply passage and penetrating the outer peripheral wall of the eccentric portion, wherein the center of the body a projection point of the axis on a reference plane perpendicular to a central axis of the body is O, a projection point of the central axis of the eccentric portion on the reference plane is A, and a central axis of the oil outlet
  • the intersection point of the peripheral wall of the eccentric portion is B, the angle between the line BO of the intersection point B and the projection point O and the line OA of the projection point O and the projection point A is ⁇ , wherein The ⁇ satisfies: Where e is an eccentricity between the body and the
  • a crankshaft for a rotary compressor is provided by setting an angle satisfying the above relationship ⁇ , when the crankshaft is applied to the rotary compressor, it does not affect the oil film distribution and the bearing of the oil film between the eccentric portion and the piston sleeved outside the eccentric portion, thereby ensuring lubrication and bearing between the eccentric portion and the piston. Avoid wear and tear.
  • an angle between the line BA of the intersection point B and the projection point A and an extension line of the line OA of the projection point A and the projection point A is ⁇ .
  • the ⁇ satisfies: 30° ⁇ ⁇ ⁇ 150°.
  • the outer peripheral wall of the eccentric portion is formed with a concave portion.
  • both ends of the concave portion in the axial direction of the eccentric portion penetrate the axial end faces of the eccentric portion, respectively.
  • the concave portion is formed inwardly recessed by a portion of the outer peripheral wall of the eccentric portion.
  • the oil outlet extends through the recess.
  • the recesses are one or more.
  • a rotary compressor according to an embodiment of the second aspect of the present invention includes a crankshaft for a rotary compressor according to the above-described first aspect of the present invention.
  • FIG. 1 is a partial perspective view of a crankshaft for a rotary compressor in accordance with an embodiment of the present invention
  • Figure 2 is a cross-sectional view taken along line A-A of Figure 1;
  • Figure 3 is a partial perspective view of a crankshaft for a rotary compressor in accordance with another embodiment of the present invention.
  • Figure 4 is a cross-sectional view taken along line B-B of Figure 3;
  • Figure 5 is a partial perspective view of a crankshaft for a rotary compressor in accordance with still another embodiment of the present invention.
  • Figure 6 is a cross-sectional view taken along line C-C of Figure 5.
  • first and second are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, features defining “first” and “second” may include one or more of the features either explicitly or implicitly. In the description of the present invention, "a plurality” means two or more unless otherwise stated.
  • connection is to be understood broadly, and may be fixed or detachable, for example, unless otherwise explicitly defined and defined. Connections, or integral connections; may be directly connected, or may be indirectly connected through an intermediate medium, and may be internal to the two elements. The specific meaning of the above terms in the present invention can be understood in a specific case by those skilled in the art.
  • crankshaft 100 for a rotary compressor will now be described with reference to Figs.
  • the crankshaft 100 can be used in a rotary compressor such as a rolling piston compressor or a rocking compressor.
  • a crankshaft 100 for a rotary compressor includes a body 1 and an eccentric portion 2.
  • the body 1 is formed with an oil supply passage 11.
  • the oil supply passage 11 may extend in the axial direction of the body 1 and penetrate the axial end faces of the body 1, but is not limited thereto.
  • the crankshaft 100 is applied to a rotary compressor, the oil supply passage 11 can supply the lubricating oil in the oil pool of the rotary compressor to the respective friction pairs in the rotary compressor for lubrication.
  • the eccentric portion 2 is formed in a cylindrical shape, and the eccentric portion 2 is sleeved on the body 1.
  • the central axis of the eccentric portion 2 is eccentrically disposed with respect to the central axis of the body 1, that is, on the cross section of the crankshaft 100, the central axis of the eccentric portion 2
  • the central axis of the body 1 is spaced apart from each other.
  • the eccentric portion 2 and the body 1 are preferably integrally formed.
  • An oil outlet hole 21 that communicates with the oil supply passage 11 and penetrates the outer peripheral wall of the eccentric portion 2 is formed in the eccentric portion 2.
  • the inner end of the oil outlet hole 21 is in communication with the oil supply passage 11, and the outer end of the oil discharge hole 21 is penetrated.
  • the outer peripheral wall of the core portion 2 whereby the lubricating oil in the oil supply passage 11 enters between the eccentric portion 2 and the piston sleeved outside the eccentric portion 2 through the oil outlet hole 21, thereby improving the eccentric portion 2 and the piston Lubrication between them reduces friction loss.
  • the direction “inner” can be understood as a direction toward the center of the body 1, and the opposite direction is defined as “outer”, that is, a direction away from the center of the body 1.
  • the projection point of the central axis of the body 1 on the reference plane perpendicular to the central axis of the body 1 is O
  • the projection point of the central axis of the eccentric portion 2 on the reference plane is A
  • the intersection of the central axis of the oil hole 21 and the outer peripheral wall of the eccentric portion 2 is B
  • the line OA between the projection point O and the projection point A is ⁇ , where ⁇ Satisfy:
  • crankshaft 100 for a rotary compressor by setting the included angle ⁇ satisfying the above relationship, when the crankshaft 100 is applied to the rotary compressor, the eccentric portion 2 and the eccentric portion are not affected.
  • the oil film distribution between the outer pistons and the bearing of the oil film can ensure the lubrication and bearing between the eccentric portion 2 and the piston, avoiding abnormal wear, thereby improving the service life of the crankshaft 100.
  • the angle between the line BA of the intersection point B and the projection point A and the extension line of the line OA of the projection point A and the projection point A is ⁇ , for better
  • ⁇ it is possible to set ⁇ to satisfy: 30° ⁇ ⁇ ⁇ 150°.
  • the oil outlet hole 21 is relatively small in pressure, the effective bearing area where the outer peripheral wall of the eccentric portion 2 is subjected to the load is not damaged.
  • the oil film of the peripheral wall of the eccentric portion 2 which is far away from the central axis of the body 1 is maintained, and the local anti-pressure working temperature friction coefficient PV value is prevented from being excessively large, thereby effectively reducing the working load of the rotary compressor.
  • the outer peripheral wall of the eccentric portion 2 is formed with a concave portion 22, and referring to FIG. 3 in conjunction with FIG. 4, the concave portion 22 may be formed by a concave portion of the outer peripheral wall of the eccentric portion 2 inwardly.
  • the central angle of the concave portion 22 corresponds to less than 360°.
  • the recessed portion 22 is one, and both ends of the recessed portion 22 in the axial direction of the eccentric portion 2 penetrate the axial end faces of the eccentric portion 2, respectively. Thereby, the processing is facilitated, and the eccentric portion 2 is further reduced The contact area between the outer peripheral wall and the inner peripheral wall of the piston.
  • the recessed portion 22 may be plural (not shown), and the plurality of recessed portions 22 may be spaced apart from each other in the circumferential direction of the eccentric portion 2, or may be disposed at the eccentric portion 2 They are arranged spaced apart from one another in the axial direction and can also be arranged at the same time in the circumferential and axial directions of the eccentric portion 2 . It can be understood that the arrangement of the recessed portion 22 on the eccentric portion 2 and the like can be specifically set according to actual requirements, and the present invention does not particularly limit this.
  • the recessed portion 22 may be integrally formed by casting, or may be formed by a milling process of a predetermined region of the outer peripheral wall of the eccentric portion 2.
  • the oil outlet hole 21 penetrates the recessed portion 22, and specifically, the outer end of the oil outlet hole 21 penetrates the inner wall of the recessed portion 22. Therefore, the partial anti-pressure working temperature friction coefficient PV value can be further prevented from being excessively large, the working load of the rotary compressor can be effectively reduced, and the oil discharge flow area is increased, and the eccentric portion 2 and the piston are better ensured. Lubrication between.
  • crankshaft 100 for a rotary compressor has the advantages of simple process, convenient processing, and the like, and the cost is effectively reduced.
  • a rotary compressor according to an embodiment of the second aspect of the present invention includes a crankshaft 100 for a rotary compressor according to the above-described first aspect of the present invention.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

公开了一种用于回转式压缩机的曲轴，曲轴（100）包括本体（1）和偏心部（2），本体（1）上形成有供油通道（11）；偏心部（2）上形成有与供油通道（11）连通且贯穿偏心部（2）的外周壁的出油孔（21），本体（1）的中心轴线在垂直于本体（1）的中心轴线所在的基准平面上的投影点为O，偏心部（2）的中心轴线在基准平面上的投影点为A，出油孔（21）的中心轴线与偏心部（2）的外周壁的交点为B，交点B与投影点O的连线BO和投影点O与投影点A的连线OA之间的夹角为θ，其中θ满足式1 ，e为本体（1）与偏心部（2）之间的偏心距，R为偏心部（2）的半径。还公开了一种具有该曲轴的回转式压缩机。该曲轴可以保证偏心部与活塞之间的润滑与承载，避免磨损。

Description

用于回转式压缩机的曲轴和具有其的回转式压缩机 技术领域
本发明涉及压缩机领域，尤其是涉及一种用于回转式压缩机的曲轴和具有其的回转式压缩机。
背景技术
相关技术中指出，回转式压缩机的偏心部为圆柱形，活塞套设在该偏心部的外周面上，且活塞的整个内圆周面与偏心部的整个外圆周面接触。当偏心部带动活塞转动时，存在摩擦损失，因此偏心部上设置有油孔，以改善偏心部与活塞之间的润滑情况。
然而，在回转式压缩机运转过程中，活塞承受高低压差气体力，并通过活塞与偏心部间的油膜传递给偏心部。由于在不同区域，偏心部外圆周面承载大小不一样，而油孔的位置会影响到油膜分布，甚至破坏油膜的承载，产生异常磨损。另外，由于偏心部带动活塞转动时存在摩擦损失，从而导致回转式压缩机的工作负荷升高。
发明内容
本发明旨在至少解决现有技术中存在的技术问题之一。为此，本发明需要提供一种用于回转式压缩机的曲轴，所述曲轴的使用寿命长。
本发明还需要提供一种具有上述曲轴的回转式压缩机。
根据本发明第一方面实施例的用于回转式压缩机的曲轴，包括：本体，所述本体上形成有供油通道；和偏心部，所述偏心部套设在所述本体上，所述偏心部的中心轴线相对于所述本体的中心轴线偏心设置，所述偏心部上形成有与所述供油通道连通且贯穿所述偏心部的外周壁的出油孔，其中所述本体的中心轴线在垂直于所述本体的中心轴线所在的基准平面上的投影点为O，所述偏心部的中心轴线在所述基准平面上的投影点为A，所述出油孔的中心轴线与所述偏心部的外周壁的交点为B，所述交点B与所述投影点O的连线BO和所述投影点O与所述投影点A的连线OA之间的夹角为θ，其中所述θ满足：
Figure PCTCN2015081266-appb-000001
其中，e为所述本体与所述偏心部之间的偏心距，R为所述偏心部的半径。
根据本发明实施例的用于回转式压缩机的曲轴，通过设置满足上述关系式的夹角 θ，当曲轴应用于回转式压缩机上时，不会影响偏心部与套设在偏心部外的活塞之间的油膜分布及油膜的承载，从而可以保证偏心部与活塞之间的润滑与承载，避免磨损。
根据本发明的一个示例，所述交点B与所述投影点A的连线BA和所述投影点O与所述投影点A的连线OA的延长线之间的夹角为β，其中所述β满足：30°≤β≤150°。
根据本发明的一个示例，所述偏心部的外周壁上形成有凹入部。
根据本发明的一个示例，所述凹入部的在所述偏心部的轴向上的两端分别贯穿所述偏心部的轴向两端端面。
根据本发明的一个示例，所述凹入部由所述偏心部的外周壁的一部分向内凹入形成。
根据本发明的一个示例，所述出油孔贯穿所述凹入部。
根据本发明的一个示例，所述凹入部为一个或多个。
根据本发明第二方面实施例的回转式压缩机，包括根据本发明上述第一方面实施例的用于回转式压缩机的曲轴。
本发明的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本发明的实践了解到。
附图说明
本发明的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1是根据本发明实施例的用于回转式压缩机的曲轴的局部立体图；
图2是沿图1中A-A线的剖面图；
图3是根据本发明另一个实施例的用于回转式压缩机的曲轴的局部立体图；
图4是沿图3中B-B线的剖面图；
图5是根据本发明再一个实施例的用于回转式压缩机的曲轴的局部立体图；
图6是沿图5中C-C线的剖面图。
附图标记：
100：曲轴；
1：本体；11：供油通道；
2：偏心部；21：出油孔；22：凹入部。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，仅用于解释本发明，而不能理解为对本发明的限制。
在本发明的描述中，需要理解的是，术语“中心”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本发明的描述中，除非另有说明，“多个”的含义是两个或两个以上。
在本发明的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本发明中的具体含义。
下面参考图1-图6描述根据本发明实施例的用于回转式压缩机的曲轴100。其中，曲轴100可以用于回转式压缩机例如滚动活塞式压缩机或摇摆式压缩机等上。
如图1、图3和图5所示，根据本发明第一方面实施例的用于回转式压缩机的曲轴100，包括本体1和偏心部2。
具体而言，本体1上形成有供油通道11，例如，供油通道11可以沿本体1的轴向延伸且贯穿本体1的轴向两端端面，但不限于此。当曲轴100应用于回转式压缩机上时，供油通道11可以将回转式压缩机的油池内的润滑油供入到回转式压缩机内的各个摩擦副以进行润滑。
偏心部2形成为圆柱体形状，偏心部2套设在本体1上，偏心部2的中心轴线相对于本体1的中心轴线偏心设置，即在曲轴100的横截面上、偏心部2的中心轴线与本体1的中心轴线彼此间隔开。其中，偏心部2与本体1优选一体成型。
偏心部2上形成有与供油通道11连通且贯穿偏心部2的外周壁的出油孔21。例如，参照图2、图4和图6，出油孔21的内端与供油通道11连通，出油孔21的外端贯穿偏 心部2的外周壁，由此，供油通道11内的润滑油会通过出油孔21进入到偏心部2与套设在偏心部2外的活塞之间，从而改善偏心部2与活塞之间的润滑，减小摩擦损失。这里，需要说明的是，方向“内”可以理解为朝向本体1中心的方向，其相反方向被定义为“外”，即远离本体1中心的方向。
其中，如图2所示，本体1的中心轴线在垂直于本体1的中心轴线所在的基准平面上的投影点为O，偏心部2的中心轴线在上述基准平面上的投影点为A，出油孔21的中心轴线与偏心部2的外周壁的交点为B，交点B与投影点O的连线BO和投影点O与投影点A的连线OA之间的夹角为θ，其中θ满足：
Figure PCTCN2015081266-appb-000002
其中，e为本体1与偏心部2之间的偏心距，R为偏心部2的半径。由此，通过使夹角θ满足上述关系式，可以保证活塞与偏心部2的有效润滑与承载。
根据本发明实施例的用于回转式压缩机的曲轴100，通过设置满足上述关系式的夹角θ，当曲轴100应用于回转式压缩机上时，不会影响偏心部2与套设在偏心部2外的活塞之间的油膜分布及油膜的承载，从而可以保证偏心部2与活塞之间的润滑与承载，避免异常磨损，进而提高了曲轴100的使用寿命。
根据本发明的进一步实施例，如图2所示，交点B与投影点A的连线BA和投影点O与投影点A的连线OA的延长线之间的夹角为β，为了更好地确保偏心部2与活塞之间的润滑，可以设置β满足：30°≤β≤150°。
由此，由于出油孔21承压相对较小，从而不会破坏偏心部2的外周壁承受载荷的有效承载区。例如，偏心部2的与本体1的中心轴线距离较远的部分外周壁的油膜保持，避免局部抗压强工作温度摩擦系数PV值过大，进而有效降低了回转式压缩机的工作负荷。
根据本发明的一个可选实施例，偏心部2的外周壁上形成有凹入部22，参照图3并结合图4，凹入部22可以由偏心部2的外周壁的一部分向内凹入形成，凹入部22对应的圆心角小于360°。由此，通过设置凹入部22，可以有效减小偏心部2的外周壁与活塞的内周壁的接触面积，从而有效减小上述两者之间的摩擦，降低回转式压缩机工作时的负荷以及噪音，进而提高了回转式压缩机的能效。
在图3和图4的示例中，凹入部22为一个，且凹入部22的在偏心部2的轴向上的两端分别贯穿偏心部2的轴向两端端面。由此，方便加工，且进一步减小了偏心部2 的外周壁与活塞的内周壁的接触面积。
当然，在本发明的其它示例中，凹入部22还可以为多个(图未示出)，多个凹入部22可以在偏心部2的周向上彼此间隔开设置，也可以在偏心部2的轴向上彼此间隔开设置，还可以同时在偏心部2的周向和轴向上彼此间隔开设置。可以理解，凹入部22在偏心部2上的布置方式等可以根据实际要求而具体设置，本发明对此不作特殊限定。
其中，凹入部22可以通过浇铸一体形成，也可以通过对偏心部2的外周壁的预定区域进行铣削工艺形成。
参照图5并结合图6，出油孔21贯穿凹入部22，具体而言，出油孔21的外端贯穿凹入部22的内壁。由此，可以进一步避免局部抗压强工作温度摩擦系数PV值过大，有效降低回转式压缩机的工作负荷，而且，增大了出油流通面积，更好地保证了偏心部2与活塞之间的润滑。
根据本发明实施例的用于回转式压缩机的曲轴100，具有工艺简单、加工方便等优点，且有效降低了成本。
根据本发明第二方面实施例的回转式压缩机，包括根据本发明上述第一方面实施例的用于回转式压缩机的曲轴100。
根据本发明实施例的回转式压缩机的其他构成例如电机等以及操作对于本领域技术人员而言都是已知的，这里不再详细描述。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示意性实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例，本领域的普通技术人员可以理解：在不脱离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本发明的范围由权利要求及其等同物限定。

Claims (8)

  1. 一种用于回转式压缩机的曲轴，其特征在于，包括：
    本体，所述本体上形成有供油通道；和
    偏心部，所述偏心部套设在所述本体上，所述偏心部的中心轴线相对于所述本体的中心轴线偏心设置，所述偏心部上形成有与所述供油通道连通且贯穿所述偏心部的外周壁的出油孔，
    其中所述本体的中心轴线在垂直于所述本体的中心轴线所在的基准平面上的投影点为O，所述偏心部的中心轴线在所述基准平面上的投影点为A，所述出油孔的中心轴线与所述偏心部的外周壁的交点为B，所述交点B与所述投影点O的连线BO和所述投影点O与所述投影点A的连线OA之间的夹角为θ，其中所述θ满足：
    Figure PCTCN2015081266-appb-100001
    其中，e为所述本体与所述偏心部之间的偏心距，R为所述偏心部的半径。
  2. 根据权利要求1所述的用于回转式压缩机的曲轴，其特征在于，所述交点B与所述投影点A的连线BA和所述投影点O与所述投影点A的连线OA的延长线之间的夹角为β，其中所述β满足：30°≤β≤150°。
  3. 根据权利要求1或2所述的用于回转式压缩机的曲轴，其特征在于，所述偏心部的外周壁上形成有凹入部。
  4. 根据权利要求3所述的用于回转式压缩机的曲轴，其特征在于，所述凹入部的在所述偏心部的轴向上的两端分别贯穿所述偏心部的轴向两端端面。
  5. 根据权利要求3所述的用于回转式压缩机的曲轴，其特征在于，所述凹入部由所述偏心部的外周壁的一部分向内凹入形成。
  6. 根据权利要求3所述的用于回转式压缩机的曲轴，其特征在于，所述出油孔贯穿所述凹入部。
  7. 根据权利要求3所述的用于回转式压缩机的曲轴，其特征在于，所述凹入部为一个或多个。
  8. 一种回转式压缩机，其特征在于，包括根据权利要求1-7中任一项所述的用于回转式压缩机的曲轴。
PCT/CN2015/081266 2015-06-11 2015-06-11 用于回转式压缩机的曲轴和具有其的回转式压缩机 WO2016197373A1 (zh)

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