WO2018218944A1 - 往复式压缩机的压缩机构及往复式压缩机 - Google Patents

往复式压缩机的压缩机构及往复式压缩机 Download PDF

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Publication number
WO2018218944A1
WO2018218944A1 PCT/CN2017/118714 CN2017118714W WO2018218944A1 WO 2018218944 A1 WO2018218944 A1 WO 2018218944A1 CN 2017118714 W CN2017118714 W CN 2017118714W WO 2018218944 A1 WO2018218944 A1 WO 2018218944A1
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WO
WIPO (PCT)
Prior art keywords
crankshaft
eccentric
compression mechanism
reciprocating compressor
eccentric sleeve
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PCT/CN2017/118714
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English (en)
French (fr)
Inventor
黄刚
严志奇
Original Assignee
安徽美芝制冷设备有限公司
美的集团股份有限公司
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Priority claimed from CN201710392294.0A external-priority patent/CN106996363B/zh
Priority claimed from CN201720614881.5U external-priority patent/CN206770163U/zh
Application filed by 安徽美芝制冷设备有限公司, 美的集团股份有限公司 filed Critical 安徽美芝制冷设备有限公司
Publication of WO2018218944A1 publication Critical patent/WO2018218944A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00

Definitions

  • the present invention relates to the field of compressors, and more particularly to a compression mechanism and a reciprocating compressor of a reciprocating compressor.
  • the present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention proposes a compression mechanism of a reciprocating compressor, the amount of refrigeration of which can be changed by a change in the direction of rotation of the crankshaft.
  • the present invention also provides a reciprocating compressor having the above-described compression mechanism.
  • a compression mechanism of a reciprocating compressor includes: a crankshaft having an eccentric portion; and a connecting rod, the two ends of the connecting rod being a crank connecting portion and a piston connecting portion, respectively, the crank connecting portion a jacket on the eccentric portion; a piston connected to the piston connecting portion; a crankshaft eccentric sleeve, the crankshaft eccentric sleeve being disposed between the crankshaft connecting portion and the eccentric portion, the crankshaft eccentric sleeve a clearance fit with the eccentric portion, a clearance fit between the crankshaft eccentric sleeve and the crankshaft connection portion, an eccentric amount between the inner peripheral wall and the outer peripheral wall of the crankshaft eccentric sleeve; a crank lock structure, The crank lock structure is disposed between the crankshaft eccentric sleeve and the crankshaft, and the crank lock structure can lock the crankshaft eccentric sleeve at different angles of the crankshaft when the crankshaft rotation direction is different The position is such that the stroke of
  • the crank lock structure can lock the eccentric sleeve of the crankshaft at different angular positions of the crankshaft when the crankshaft rotation direction is different, so that the crankshaft eccentric sleeve The eccentricity amount superimposed on the eccentric portion of the crankshaft is different, so that the stroke of the piston is different, and the compression amount of the compression mechanism is changed, thereby achieving the purpose of achieving a double cooling capacity of the compression mechanism.
  • the inner peripheral wall of the crankshaft eccentric sleeve is provided with a notch
  • the crank lock structure includes an eccentric shaft pin connected to the eccentric portion and fitted in the notch, The eccentric pin in the direction of rotation can respectively stop against the opposite side walls of the notch in the circumferential direction.
  • the opposite side walls of the notch in the circumferential direction are respectively disposed corresponding to the maximum thickness and the minimum thickness of the eccentric sleeve of the crankshaft.
  • the eccentric shaft pin is disposed on a line connecting the center of rotation of the crankshaft and the center of the eccentric portion.
  • crankshaft is provided with an eccentric shaft pin hole, and one end of the eccentric shaft pin is fitted in the eccentric shaft pin hole.
  • crankshaft and the eccentric shaft pin are fixedly connected by an elastic pin.
  • the angle of rotation of the eccentric shaft pin relative to the axis of rotation of the crankshaft is 180 degrees.
  • the eccentric shaft pin is disposed on a side of the crankshaft eccentric sleeve that is away from the balance portion of the crankshaft.
  • crankshaft eccentric sleeve is provided with a bushing oil hole penetrating in the thickness direction.
  • a reciprocating compressor according to an embodiment of the present invention includes a compression mechanism of a reciprocating compressor according to the above embodiment of the present invention.
  • the stroke of the compressor piston can be changed by the way of positive and negative rotation of the crankshaft, and the effect of the two volumes of refrigeration of one compressor can be achieved.
  • Figure 1 is an exploded view of a compression mechanism in accordance with an embodiment of the present invention.
  • Fig. 2 is a structural view of a crankcase according to an embodiment of the present invention.
  • Fig. 3 is a structural view of a link of an embodiment of the present invention.
  • FIG. 4 is an exploded view of a partial part of a compression mechanism in accordance with an embodiment of the present invention.
  • Fig. 5 is a structural view showing an eccentric sleeve of a crankshaft according to an embodiment of the present invention.
  • Figure 6 is a schematic view of the embodiment of the present invention when the crankshaft forward rotation piston is at top dead center.
  • Figure 7 is a schematic view of the embodiment of the present invention when the crankshaft forward rotation piston is at the bottom dead center.
  • Figure 8 is a schematic view of the embodiment of the present invention when the crankshaft reversing piston is at top dead center.
  • Figure 9 is a schematic view of the embodiment of the present invention when the crankshaft reversing piston is at the bottom dead center.
  • Figure 10 is a perspective structural view of a crankshaft eccentric bushing according to an embodiment of the present invention.
  • crankcase 1 crankshaft shaft hole 11
  • piston cylinder bore 12 crankcase 1
  • crankshaft 2 an eccentric portion 21, an eccentric pin hole 22, a fitting hole 23, a balance portion 24,
  • a connecting rod 3 a crank connecting portion 31, a piston connecting portion 32, a piston 4, a piston pin 41,
  • a compression mechanism 100 in accordance with an embodiment of the present invention will now be described with reference to Figs.
  • a compression mechanism 100 includes a crankshaft 2, a connecting rod 3, a piston 4, a crankshaft eccentric sleeve 5, and a locking mechanism.
  • the crankshaft 2 has an eccentric portion 21.
  • the two ends of the connecting rod 3 are respectively a crank connecting portion 31 and a piston connecting portion 32.
  • the crank connecting portion 31 is jacketed on the eccentric portion 21, and the piston connecting portion 32 is connected to the piston 4.
  • crank eccentric sleeve 5 is sleeved between the crank connecting portion 31 and the eccentric portion 21, and the crank eccentric sleeve 5 and the eccentric portion 21 are gap-fitted therebetween, and between the crank eccentric sleeve 5 and the crank connecting portion 31 is
  • the clearance fit has an eccentric amount between the inner peripheral wall and the outer peripheral wall of the crankshaft eccentric sleeve 5.
  • crank lock structure is disposed between the crankshaft eccentric sleeve 5 and the crankshaft 2.
  • the crank lock structure can lock the crankshaft eccentric sleeve 5 at different angular positions of the crankshaft 2, In order to make the stroke of the piston 4 different.
  • crankshaft eccentric sleeve 5 is rotatable about the axis of rotation of the crankshaft 2 under the action of friction.
  • crankshaft eccentric sleeve 5 When the crankshaft 2 is rotated in the first direction, the crankshaft eccentric sleeve 5 is rotated by a first set angle with respect to the crankshaft 2, and the crankshaft lock structure is triggered to be locked at the first angular position of the crankshaft 2. Thereafter, the crankshaft 2 continues to rotate, at which time the crankshaft eccentric sleeve 5 has been locked to the crankshaft 2, and the crankshaft eccentric sleeve 5 rotates synchronously with the crankshaft 2. Thereby, the crankshaft 2 rotates to drive the link 3, and the link 3 drives the piston 4 to move up and down, and the stroke is the first stroke.
  • crankshaft eccentric sleeve 5 When the crankshaft 2 rotates in the second direction, the crankshaft eccentric sleeve 5 rotates the second set angle with the crankshaft 2, and then triggers the crankshaft locking structure to be locked at the second angular position of the crankshaft 2, after which the crankshaft 2 The rotation continues, at which time the crankshaft eccentric sleeve 5 has been locked to the crankshaft 2, and the crankshaft eccentric sleeve 5 rotates synchronously with the crankshaft 2. Thereby, the crankshaft 2 rotates to drive the link 3, and the link 3 drives the piston 4 to move up and down, and the stroke is the second stroke.
  • the stroke of the piston 4 is determined by superimposing the eccentric amount of the eccentric portion 21 of the crankshaft 2 and the eccentric amount of the crank eccentric sleeve 5. Therefore, if the first angular position and the second angular position of the crankshaft eccentric locking mechanism 5 are different, the superposition result of the eccentric amount of the eccentric portion 21 of the crankshaft 2 and the eccentric amount of the crankshaft eccentric sleeve 5 may be Differently, the stroke of the piston 4 will not be the same.
  • the crankshaft lock structure can lock the crankshaft eccentric sleeve 5 at different angular positions of the crankshaft 2 when the crankshaft 2 rotates in different directions.
  • the eccentricity of the crankshaft eccentric sleeve 5 superimposed on the eccentric portion 21 of the crankshaft 2 is different, so that the stroke of the piston 4 is different, and the compression amount of the compression mechanism is changed, thereby achieving the purpose of achieving a double cooling capacity of the compression mechanism.
  • the inner peripheral wall of the crankshaft eccentric sleeve 5 is provided with a notch 51, and the crank eccentric sleeve 5 constitutes a boss boss 52 in the remaining portion of the circumferential direction corresponding to the notch 51.
  • the crankshaft locking structure includes an eccentric shaft pin 6 fitted in the notch 51.
  • the eccentric shaft pins 6 can be respectively stopped on the opposite side walls of the notch 51 in the circumferential direction in the two rotational directions of the crankshaft 2.
  • the eccentric shaft pin 6 is connected to the crankshaft 2.
  • the eccentric shaft pin 6 can rotate with the crankshaft 2, and after rotating a certain angle, the eccentric shaft pin 6 can stop against the axis of the crankshaft eccentric sleeve 5.
  • the locking of the eccentric shaft pin 6 and the crankshaft 2 is completed.
  • This angular position of the crankshaft eccentric sleeve 5 on the crankshaft 2 when defining the lock is very simple and easy to machine.
  • the first direction in which the crankshaft 2 rotates is referred to as a forward direction and the second direction is a reverse direction.
  • crankshaft eccentric sleeve 5 when the crankshaft 2 rotates in the forward direction, the crankshaft eccentric sleeve 5 is locked at the first angular position of the crankshaft 2, that is, the locking surface of the crankshaft locking structure and the crankshaft eccentric sleeve 5 is the first surface 521.
  • the crankshaft eccentric sleeve 5 is locked at the second angular position of the crankshaft 2, that is, the locking surface of the crankshaft locking structure and the crankshaft eccentric sleeve 5 is the second surface 522.
  • crank lock structure when the crank lock structure is different from the lock surface of the crank eccentric sleeve 5, when the crankshaft 2 rotates, the eccentric amount of the eccentric portion 21 of the crankshaft 2 is different from the eccentric amount of the crank eccentric sleeve 5, that is, the movement stroke of the piston 4. different.
  • the notch 51 penetrates the crank eccentric sleeve 5 in the thickness direction of the crank eccentric sleeve 5, and the notch 51 penetrates the crank eccentric sleeve 5 in a direction toward one end surface of the crank eccentric sleeve 5.
  • the notch 51 is easily processed on the crank eccentric sleeve 5.
  • the notch 51 may also be formed as a blind hole or a perforation on the inner peripheral wall of the crankshaft eccentric sleeve 5, which is not limited herein.
  • the opposite side walls of the notch 51 are respectively disposed corresponding to the maximum thickness and the minimum thickness of the crank eccentric sleeve 5, so that when the crank eccentric sleeve 5 is locked at the first angular position and the second angular position At this time, the amount of eccentricity of the crankshaft eccentric sleeve 5 that can be applied to the crankshaft 2 is maximized, so that the capacity change of the compression mechanism 100 is maximized when the rotational direction of the crankshaft 2 is different.
  • the position of the notch 51 can also be adjusted as needed.
  • a plurality of notches 51 can be disposed on the crankshaft eccentric sleeve 5, and the crank eccentric sleeve 5 is applied to two compression mechanisms of the same structure, one of which The eccentric shaft pin 6 of the compression mechanism cooperates with a notch of the crankshaft eccentric sleeve 5, and the eccentric shaft pin 6 of the other compression mechanism cooperates with the other notch of the crankshaft eccentric sleeve 5, and the same two compression mechanisms eventually The amount of compression may vary.
  • the eccentric shaft pin 6 is disposed on the line connecting the center of rotation of the crankshaft 2 and the center of the eccentric portion 21, so that the eccentric amount of the eccentric shaft pin 6 can be superimposed with the maximum eccentric amount of the crankshaft 2, thereby obtaining the maximum superposition result.
  • the angle of rotation of the eccentric shaft pin 6 with respect to the axis of rotation of the crankshaft 2 is 180 degrees. In this way, the circumferential length of the crankshaft eccentric sleeve 5 can be fully utilized to lay out the thickness variation of the crankshaft eccentric sleeve 5.
  • the radius of the inner peripheral wall of the boss boss 52 is larger than the radius of the inner peripheral wall of the remaining portion; the radius of the outer peripheral wall of the boss boss 52 is smaller than the radius of the outer peripheral wall of the remaining portion.
  • the crankshaft eccentric sleeve 5 is provided with a bushing oil hole 53 penetrating in the thickness direction.
  • the lubricating oil enters the matching gap between the eccentric sleeve 5 of the crankshaft and the connecting rod 3 through the sleeve oil hole 53 to play a lubricating role.
  • the crankshaft 2 is provided with an eccentric shaft pin bore 22 with one end of the eccentric shaft pin 6 mated within the eccentric shaft pin bore 22.
  • This plug connection method facilitates the independent processing of the crankshaft 2 and the eccentric shaft pin 6, ensuring the machining accuracy of both.
  • the eccentric shaft pin 6 is connected to the crankshaft 2 in various manners.
  • the eccentric shaft pin 6 may be fixed to the crankshaft 2 by welding, or riveted to the crankshaft 2.
  • the crankshaft 2 and the eccentric shaft pin 6 are connected and fixed by a connecting member.
  • the connecting member is an elastic pin 7, which is connected by an elastic pin, has good elasticity and shear resistance, and the connection is reliable and stable.
  • the eccentric shaft pin hole 22 is formed as a threaded hole, and the eccentric shaft pin 6 is provided with a thread, and the eccentric shaft pin 6 is fixed to the crankshaft 2 by a screw connection, that is, a part of the eccentric shaft pin 6 is formed as a screw connection.
  • the eccentric shaft pin 6 is disposed on a side of the crankshaft eccentric sleeve 5 that is remote from the balance portion 24 of the crankshaft 2.
  • the eccentric shaft pin 6 corresponds to the engagement of the crank eccentric sleeve 5 on the balance portion 24 of the crankshaft 2, thereby improving the connection reliability.
  • the crank lock structure may not be limited to the above structure.
  • the chute may be disposed on the end surface of the balance portion 24 facing the crank eccentric sleeve 5, and then the slide is disposed on the opposite end faces of the crank eccentric sleeve 5.
  • the column and the chute can be arranged according to the trajectory of the crankshaft eccentric sleeve 5 when the crankshaft 2 rotates, and the chute has two extreme positions.
  • the crankshaft eccentric sleeve 5 is rotated to an extreme position, the spool is locked at the first angular position.
  • the crankshaft eccentric sleeve 5 is rotated to another extreme position, the spool is locked at the second angular position.
  • a compression mechanism 100 in accordance with one embodiment of the present invention will now be described with reference to Figs.
  • the compression mechanism 100 in this embodiment is composed of a crankcase 1, a crankshaft 2, a crankshaft eccentric sleeve 5, a link 3, an elastic pin 7, an eccentric shaft pin 6, a piston pin 41, and a piston 4.
  • the crankcase 1 is provided with a crankshaft hole 11 and a piston cylinder bore 12.
  • the crankshaft 2 is coaxially and clearance-fitted with the crankshaft bore 11, and the piston 4 is fitted into the piston bore 12 by means of a clearance fit.
  • the crankshaft eccentric sleeve 5 is coaxially assembled with the eccentric portion 21 of the crankshaft 2, and there is a matching gap between the crankshaft eccentric sleeve 5 and the eccentric portion 21 of the crankshaft 2, and the crankshaft eccentric sleeve 5 is rotatable around the eccentric portion 21 of the crankshaft 2 while the crankshaft
  • the eccentric sleeve 5 rotates with the crankshaft 2 about the rotation axis of the crankshaft 2.
  • the crankshaft eccentric sleeve 5 is provided with a ring of different centers, and the inner circle of the crankshaft eccentric sleeve 5 is S0 relative to the outer circle.
  • crank connecting portion 31 of the link 3 is disposed coaxially with the crank eccentric sleeve 5, and a clearance fit is provided between the crank connecting portion 31 and the crank eccentric sleeve 5.
  • the eccentric portion 21 of the crankshaft 2, the crank eccentric sleeve 5, and the crank connecting portion 31 of the link 3 are rotatable about the axis of the eccentric portion 21 of the crankshaft 2.
  • the crankshaft 2 is provided with an eccentric shaft pin hole 22.
  • the eccentric shaft pin 6 is inserted into the eccentric shaft pin hole 22, and the elastic pin 7 is inserted into the elastic pin.
  • the 7-hole and the engaging hole 23 in the eccentric shaft pin 6 fix the eccentric shaft pin 6 to the crankshaft 2, and the eccentric shaft pin 6 is rotatable with the crankshaft 2.
  • the piston 4 is interleaved with the piston cylinder bore 12, the piston connecting portion 32 of the connecting rod 3 is inserted into the intermediate portion of the piston 4, and the piston pin 41 is connected to the connecting rod 3 through the piston 4 and the piston connecting portion 32.
  • the compression mechanism 100 of the present embodiment changes the stroke of the piston 4 by means of the positive and negative rotation of the crankshaft 2 to achieve the effect that one compression mechanism has two volumetric cooling capacities.
  • the compression mechanism 100 in this embodiment locks the crankshaft eccentric sleeve 5 by the eccentric shaft pin 6, and changes the stroke of the piston 4, so that the stroke difference between the positive and negative pistons 4 of the crankshaft 2 is four times that of the eccentric sleeve 5 of the crankshaft, and the compression process is realized.
  • the change in the volume of the refrigerant discharged is realized.
  • a reciprocating compressor according to an embodiment of the present invention includes a compression mechanism 100 of a reciprocating compressor according to the above embodiment of the present invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

一种往复式压缩机的压缩机构，压缩机构（100）包括曲轴（2）、活塞（4）、曲轴偏心套（5）和锁合机构。曲轴（2）具有偏心部（21），连杆（3）的两端分别为曲轴连接部（31）和活塞连接部（32），曲轴连接部（31）外套在偏心部（21）上。曲轴偏心套（5）套设在曲轴连接部（31）和偏心部（21）之间。锁合结构设在曲轴偏心套（5）和曲轴（2）之间，当曲轴（2）转动方向不同时锁合结构可将曲轴偏心套（5）锁止在曲轴（2）的不同角度位置处，以使活塞（4）的行程不同。该压缩机构具有双制冷量。还公开了一种往复式压缩机。

Description

往复式压缩机的压缩机构及往复式压缩机 技术领域
本发明涉及压缩机领域，尤其涉及一种往复式压缩机的压缩机构及往复式压缩机。
背景技术
如家用电冰箱、房间空调器等小型制冷设备的发展，是衡量一个国家国民经济建设、科学技术以及人民生活水平的标志。近十年来，随着我国经济建设的全面发展、人民生活水平的不断提高以及先进技术的引进，新型往复式制冷压缩机产品的开发，成为各大企业抢占冰箱压缩机市场、提升产品市场竞争力的主要手段。然而全封闭往复式制冷压缩机产业的发展一直处于对现有产品的优化改善阶段，产品整体的结构形式均处于固化状态，市场中急需一种新型的全封闭往复式制冷压缩机来开拓市场，扩大制冷压缩机市场产品的多元化。
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，本发明提出一种往复式压缩机的压缩机构，所述压缩机构的制冷量可通过曲轴的转动方向的变化而改变。
本发明还在于提出一种具有上述压缩机构的往复式压缩机。
根据本发明实施例的往复式压缩机的压缩机构，包括：曲轴，所述曲轴具有偏心部；连杆，所述连杆的两端分别为曲轴连接部和活塞连接部，所述曲轴连接部外套在所述偏心部上；活塞，所述活塞与所述活塞连接部相连；曲轴偏心套，所述曲轴偏心套套设在所述曲轴连接部和所述偏心部之间，所述曲轴偏心套与所述偏心部之间为间隙配合，所述曲轴偏心套与所述曲轴连接部之间为间隙配合，所述曲轴偏心套的内周壁和外周壁之间具有偏心量；曲轴锁合结构，所述曲轴锁合结构设在所述曲轴偏心套和所述曲轴之间，当所述曲轴转动方向不同时所述曲轴锁合结构可将所述曲轴偏心套锁止在所述曲轴的不同角度位置处，以使所述活塞的行程不同。
根据本发明实施例的压缩机构，通过设置曲轴偏心套与曲轴锁合结构，可实现曲轴转动方向不同时曲轴锁合结构可将曲轴偏心套锁止在曲轴的不同角度位置处，使曲轴偏心套叠加在曲轴的偏心部上的偏心量结果不同，从而使活塞的行程不同，进而压缩机构 的压缩量发生变化，从而达到实现压缩机构具有双制冷量的目的。
在一些实施例中，所述曲轴偏心套的内周壁上设有缺口，所述曲轴锁合结构包括与所述偏心部相连且配合在所述缺口内的偏心轴销，在所述曲轴两种转动方向上所述偏心轴销可分别止抵在所述缺口在周向上的相对两侧壁上。
具体地，所述缺口在周向上的相对两侧壁分别对应所述曲轴偏心套的厚度最大处及厚度最小处设置。
更具体地，所述偏心轴销设置在所述曲轴的旋转中心和所述偏心部的中心的连线上。
可选地，所述曲轴上设有偏心轴销孔，所述偏心轴销的一端配合在所述偏心轴销孔内。
可选地，所述曲轴与所述偏心轴销之间通过弹性销相连接固定。
在一些实施例中，当所述偏心轴销分别止抵所述缺口在周向上的相对两侧壁时，所述偏心轴销相对所述曲轴的旋转轴线的转动角度为180度。
具体地，所述偏心轴销设在所述曲轴偏心套的远离所述曲轴的平衡部的一侧。
具体地，所述曲轴偏心套上设有在厚度方向上贯通的轴套油孔。
根据本发明实施例的往复式压缩机，包括根据本发明上述实施例所述的往复式压缩机的压缩机构。
根据本发明实施例的往复式压缩机，通过曲轴正反转的方式改变压缩机活塞的行程，可以实现一台压缩机两种容积制冷量的效果。
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是本发明实施例的压缩机构的爆炸视图。
图2是本发明实施例的曲轴箱的结构图。
图3是本发明实施例的连杆的结构图。
图4是本发明实施例的压缩机构的局部部件的爆炸视图。
图5是本发明实施例的曲轴偏心套的结构图。
图6是本发明实施例的当曲轴正转活塞处于上止点时的示意图。
图7是本发明实施例的当曲轴正转活塞处于下止点时的示意图。
图8是本发明实施例的当曲轴反转活塞处于上止点时的示意图。
图9是本发明实施例的当曲轴反转活塞处于下止点时的示意图。
图10是本发明实施例的曲轴偏心套的立体结构图。
附图标记：
压缩机构100、
曲轴箱1、曲轴轴孔11、活塞缸孔12、
曲轴2、偏心部21、偏心销轴孔22、配合孔23、平衡部24、
连杆3、曲轴连接部31、活塞连接部32、活塞4、活塞销41、
曲轴偏心套5、缺口51、轴套凸台52、第一面521、第二面522、轴套油孔53、
偏心轴销6、弹性销7。
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。
下面参考图1-图10描述根据本发明实施例的压缩机构100。
如图1所示，根据本发明实施例的压缩机构100，包括：曲轴2、连杆3、活塞4、曲轴偏心套5和锁合机构。
如图4所示，曲轴2具有偏心部21。连杆3的两端分别为曲轴连接部31和活塞连接部32，曲轴连接部31外套在偏心部21上，活塞连接部32与活塞4相连。
如图4所示，曲轴偏心套5套设在曲轴连接部31和偏心部21之间，曲轴偏心套5与偏心部21之间为间隙配合，曲轴偏心套5与曲轴连接部31之间为间隙配合，曲轴偏心套5的内周壁和外周壁之间具有偏心量。
如图4所示，曲轴锁合结构设在曲轴偏心套5和曲轴2之间，当曲轴2转动方向不同时曲轴锁合结构可将曲轴偏心套5锁止在曲轴2的不同角度位置处，以使活塞4的行程不同。
可以理解的是，由于曲轴偏心套5与曲轴连接部31之间为间隙配合，因此当曲轴2转动时，当曲轴锁合结构未将曲轴偏心套5和曲轴2相锁合时，曲轴偏心套5在摩擦力的作用下可以围绕曲轴2的旋转轴线旋转。
当曲轴2沿第一方向旋转时，曲轴偏心套5相对曲轴2转动第一设定角度后，触发 曲轴锁合结构，从而被锁止在曲轴2的第一角度位置处。之后，曲轴2继续旋转，此时曲轴偏心套5已经锁合在曲轴2上，曲轴偏心套5与曲轴2同步转动。由此，曲轴2旋转带动连杆3，连杆3驱动活塞4上下运动，且行程为第一行程。
当曲轴2沿第二方向旋转时，曲轴偏心套5随曲轴2转动第二设定角度后，再次触发曲轴锁合结构，从而被锁止在曲轴2的第二角度位置处，之后，曲轴2继续旋转，此时曲轴偏心套5已经锁合在曲轴2上，曲轴偏心套5与曲轴2同步转动。由此，曲轴2旋转带动连杆3，连杆3驱动活塞4上下运动，且行程为第二行程。
需要说明的是，活塞4的行程由曲轴2的偏心部21的偏心量与曲轴偏心套5的偏心量叠加决定的。因此，如果曲轴锁合结构将曲轴偏心套5锁合的第一角度位置、第二角度位置不同，上述曲轴2的偏心部21的偏心量与曲轴偏心套5的偏心量之间的叠加结果会不同，则活塞4的行程也不会相同。
根据本发明实施例的压缩机构100，通过设置曲轴偏心套5与曲轴锁合结构，可实现曲轴2转动方向不同时曲轴锁合结构可将曲轴偏心套5锁止在曲轴2的不同角度位置处，使曲轴偏心套5叠加在曲轴2的偏心部21上的偏心量结果不同，从而使活塞4的行程不同，进而压缩机构的压缩量发生变化，从而达到实现压缩机构具有双制冷量的目的。
在一些实施例中，如图5所示，曲轴偏心套5的内周壁上设有缺口51，曲轴偏心套5在缺口51对应的周向上的其余部分构成轴套凸台52。
曲轴锁合结构包括配合在缺口51内的偏心轴销6，在曲轴2两种转动方向上偏心轴销6可分别止抵在缺口51在周向上的相对两侧壁上。
可以理解的是，偏心轴销6与曲轴2相连，当曲轴2旋转时，偏心轴销6可以随着曲轴2旋转，旋转一定角度后，偏心轴销6可以止抵在曲轴偏心套5的轴套凸台52上，完成偏心轴销6与曲轴2的锁合。这种限定锁合时曲轴偏心套5在曲轴2上的角度位置，结构非常简单，容易加工。
为方便描述，下文叙述中称曲轴2转动的第一方向为正向，第二方向为反向。
由前文叙述可知，当曲轴2沿正向旋转时，曲轴偏心套5被锁止在曲轴2的第一角度位置处，即曲轴锁合结构与曲轴偏心套5的锁合面为第一面521；当曲轴2沿反向旋转时，曲轴偏心套5被锁止在曲轴2的第二角度位置处，即曲轴锁合结构与曲轴偏心套5的锁合面为第二面522。由此，曲轴锁合结构与曲轴偏心套5的锁合面不同使得曲轴2旋转时，曲轴2偏心部21的偏心量与曲轴偏心套5的偏心量的叠加方式不同，即活塞4的运动行程不同。
具体地，缺口51在曲轴偏心套5的厚度方向上贯通曲轴偏心套5，缺口51在朝向曲轴偏心套5的一个端面的方向上贯通曲轴偏心套5。这样在曲轴偏心套5上容易加工缺口51。
当然，在本发明的其他实施例中，缺口51也可以形成为曲轴偏心套5的内周壁上的盲孔或者穿孔，这里不作限制。
具体地，缺口51在周向上的相对两侧壁分别对应曲轴偏心套5的厚度最大处及厚度最小处设置，这样，当曲轴偏心套5被锁合在第一角度位置处和第二角度位置处时，曲轴偏心套5能够套加在曲轴2上的偏心量最大，从而实现当曲轴2转动方向不同时压缩机构100的容量变化最大。
当然，本发明实施例中也可根据需要调整缺口51的位置，例如，可在曲轴偏心套5上设置多个缺口51，当曲轴偏心套5应用在结构相同的两个压缩机构中，其中一个压缩机构里偏心轴销6与曲轴偏心套5的一个缺口配合，另一个压缩机构里偏心轴销6与曲轴偏心套5的另一个缺口配合，由于缺口位置不同，因此同样的两个压缩机构最终压缩量可能会不同。
这样在曲轴偏心套5应用在不同容量变化需要的压缩机构中时，可调整偏心轴销6配合的缺口51。
进一步地，偏心轴销6设置在曲轴2的旋转中心和偏心部21的中心的连线上，这样偏心轴销6的偏心量可与曲轴2的最大偏心量相叠加，从而获得最大叠加结果。
在一些实施例中，当偏心轴销6分别止抵在缺口51在周向上的相对两侧壁上时，偏心轴销6相对曲轴2的旋转轴线的转动角度为180度。这样可充分利用曲轴偏心套5的周向长度，来布局曲轴偏心套5的厚度变化。
可选地，轴套凸台52的内周壁的半径大于其余部分的内周壁半径；轴套凸台52的外周壁的半径小于其余部分的外周壁半径。由此，在对曲轴偏心套5进行精加工的过程中，能够采用无心磨工艺，且加工时无需对轴套凸台52的内外周壁进行加工，减少了精加工的面积。此外，这样的轴套凸台52还可以降低曲轴2运转过程中曲轴2的偏心部21与曲轴偏心套5、曲轴偏心套5与连杆3的曲轴连接部31之间的摩擦损失。
可选地，如图10所示，曲轴偏心套5上设有在厚度方向上贯通的轴套油孔53。压缩机构100运行过程中，润滑油经轴套油孔53进入曲轴偏心套5与连杆3的配合间隙中，起到了润滑作用。
在一些实施例中，曲轴2上设有偏心轴销孔22，偏心轴销6的一端配合在偏心轴销孔22内。这种插接连接方式，可便于曲轴2和偏心轴销6的独立加工，保证二者的加 工精度。
本发明实施例中，偏心轴销6与曲轴2的连接方式有多种，例如，偏心轴销6可以通过焊接固定在曲轴2上，或者铆接连接在曲轴2上。
在一些可选的实施例中，曲轴2与偏心轴销6之间通过连接件相连接固定。例如连接件为弹性销7，使用弹性销连接，具有良好的弹性及抗剪切力，连接可靠稳定。又例如，偏心轴销孔22形成为螺纹孔，偏心轴销6上设有螺纹，通过螺纹连接将偏心轴销6固定在曲轴2上，即偏心轴销6的一部分形成为螺纹连接件。
在一些实施例中，偏心轴销6设在曲轴偏心套5的远离曲轴2的平衡部24的一侧。这样，偏心轴销6相当于将曲轴偏心套5卡在了曲轴2的平衡部24上，提高连接可靠性。
当然，在本发明实施例中，曲轴锁合结构可不限于上述结构，例如，可在平衡部24的朝向曲轴偏心套5的端面上设置滑槽，然后在曲轴偏心套5的相对端面上设置滑柱，滑槽可按照曲轴偏心套5相对曲轴2转动时的轨迹设置，同时滑槽具有两个极限位置，当曲轴偏心套5转动至一个极限位置时被滑柱锁合在第一角度位置处，当曲轴偏心套5转动至另一个极限位置时被滑柱锁合在第二角度位置处。
下面参考图1-图10描述本发明一个具体实施例的压缩机构100。
本实施例中的压缩机构100由曲轴箱1、曲轴2、曲轴偏心套5、连杆3、弹性销7、偏心轴销6、活塞销41和活塞4组成。
如图1-图2所示，曲轴箱1上设有曲轴轴孔11和活塞缸孔12，曲轴2与曲轴轴孔11同轴且间隙配合，活塞4采用间隙配合方式装配入活塞缸孔12中，曲轴偏心套5与曲轴2的偏心部21同轴装配，曲轴偏心套5与曲轴2的偏心部21之间存在配合间隙，曲轴偏心套5可绕曲轴2的偏心部21旋转，同时曲轴偏心套5随曲轴2绕曲轴2的旋转轴线旋转，曲轴偏心套5上设有不同心的圆环，曲轴偏心套5内圆相对外圆偏心量为S0。
如图1、图3所示，连杆3的曲轴连接部31与曲轴偏心套5同轴设置，曲轴连接部31与曲轴偏心套5之间采用间隙配合。曲轴2的偏心部21、曲轴偏心套5和连杆3的曲轴连接部31之间均可绕着曲轴2的偏心部21轴线旋转。
如图1、图4所示，曲轴2上设有偏心轴销孔22，当曲轴偏心套5与连杆3装配完成后，偏心轴销6插入偏心轴销孔22，弹性销7插入弹性销7孔与偏心轴销6上的配合孔23，将偏心轴销6固定于曲轴2上，偏心轴销6可随曲轴2旋转。
活塞4与活塞缸孔12间隙转配，连杆3上的活塞连接部32插入活塞4的中间部位，活塞销41穿过活塞4与活塞连接部32将活塞4与连杆3相连接。
本实施例的压缩机构100，通过曲轴2正反转的方式改变活塞4的行程以实现一个压缩机构具有两种容积制冷量的效果。
当曲轴2正转时，带动偏心轴销6正转，曲轴偏心套5受曲轴2摩擦作用沿曲轴2的偏心部21轴线旋转，如图6所示，当活塞4运行到上止点时，偏心轴销6与轴套凸台52的第一面521相接并锁定曲轴偏心套5，此时，活塞4端面与曲轴箱1端面之间的距离为L1，活塞4在上止点时凹进活塞缸孔12内，如图7所示，当活塞4在下止点时活塞4端面与曲轴箱1端面之间的距离为L2，此时活塞4行程为曲轴2偏心量的两倍与曲轴偏心套5偏心量的两倍之和。
当曲轴2反转时，带动偏心轴销6反转，曲轴偏心套5受曲轴2摩擦作用沿曲轴2的偏心部21轴线旋转，如图8所示，当活塞4运行到上止点时，偏心轴销6与轴套凸台52的第二面522相接并锁定曲轴偏心套5，活塞4端面与曲轴箱1端面之间的距离为L3，活塞4在上止点时凸出活塞缸孔12内，如图9所示，当活塞4在下止点时，活塞4端面与曲轴箱1端面之间的距离为L4，此时活塞4行程为曲轴2偏心量两倍与曲轴偏心套5偏心量的两倍之差。
本实施例中的压缩机构100通过偏心轴销6对曲轴偏心套5闭锁，改变活塞4行程，使得曲轴2正反转活塞4行程差值为曲轴偏心套5偏心量的四倍，实现压缩过程排出冷媒容积的变化。
根据本发明实施例的往复式压缩机，包括根据本发明上述实施例所述的往复式压缩机的压缩机构100。
由此，通过原动机正反转的方式改变压缩机活塞的行程，可以实现一台压缩机两种容积制冷量的效果。
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 (10)

  1. 一种往复式压缩机的压缩机构，其特征在于，包括：
    曲轴，所述曲轴具有偏心部；
    连杆，所述连杆的两端分别为曲轴连接部和活塞连接部，所述曲轴连接部外套在所述偏心部上；
    活塞，所述活塞与所述活塞连接部相连；
    曲轴偏心套，所述曲轴偏心套套设在所述曲轴连接部和所述偏心部之间，所述曲轴偏心套与所述偏心部之间为间隙配合，所述曲轴偏心套与所述曲轴连接部之间为间隙配合，所述曲轴偏心套的内周壁和外周壁之间具有偏心量；
    曲轴锁合结构，所述曲轴锁合结构设在所述曲轴偏心套和所述曲轴之间，当所述曲轴转动方向不同时所述曲轴锁合结构可将所述曲轴偏心套锁止在所述曲轴的不同角度位置处，以使所述活塞的行程不同。
  2. 根据权利要求1所述的往复式压缩机的压缩机构，其特征在于，所述曲轴偏心套的内周壁上设有缺口，所述曲轴锁合结构包括与所述偏心部相连且配合在所述缺口内的偏心轴销，在所述曲轴两种转动方向上所述偏心轴销可分别止抵在所述缺口在周向上的相对两侧壁上。
  3. 根据权利要求2所述的往复式压缩机的压缩机构，其特征在于，所述缺口在周向上的相对两侧壁分别对应所述曲轴偏心套的厚度最大处及厚度最小处设置。
  4. 根据权利要求2所述的往复式压缩机的压缩机构，其特征在于，所述偏心轴销设置在所述曲轴的旋转中心和所述偏心部的中心的连线上。
  5. 根据权利要求2所述的往复式压缩机的压缩机构，其特征在于，所述曲轴上设有偏心轴销孔，所述偏心轴销的一端配合在所述偏心轴销孔内。
  6. 根据权利要求5所述的往复式压缩机的压缩机构，其特征在于，所述曲轴与所述偏心轴销之间通过弹性销相连接固定。
  7. 根据权利要求2所述的往复式压缩机的压缩机构，其特征在于，当所述偏心轴销分别止抵所述缺口在周向上的相对两侧壁时，所述偏心轴销相对所述曲轴的旋转轴线的转动角度为180度。
  8. 根据权利要求2所述的往复式压缩机的压缩机构，其特征在于，所述偏心轴销设在所述曲轴偏心套的远离所述曲轴的平衡部的一侧。
  9. 根据权利要求1-8任一项所述的往复式压缩机的压缩机构，其特征在于，所述 曲轴偏心套上设有在厚度方向上贯通的轴套油孔。
  10. 一种往复式压缩机，其特征在于，包括根据权利要求1-9中任一项所述的往复式压缩机的压缩机构。
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