WO2019024562A1 - 压缩机以及具有它的制冷设备 - Google Patents

压缩机以及具有它的制冷设备 Download PDF

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Publication number
WO2019024562A1
WO2019024562A1 PCT/CN2018/086371 CN2018086371W WO2019024562A1 WO 2019024562 A1 WO2019024562 A1 WO 2019024562A1 CN 2018086371 W CN2018086371 W CN 2018086371W WO 2019024562 A1 WO2019024562 A1 WO 2019024562A1
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Prior art keywords
chamber
cylinder
working chamber
piston
compressor
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PCT/CN2018/086371
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English (en)
French (fr)
Inventor
吴延平
梅佩佩
曾令华
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广东美芝制冷设备有限公司
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Publication of WO2019024562A1 publication Critical patent/WO2019024562A1/zh

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    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to the field of compressor technology, and in particular to a compressor and a refrigeration apparatus having the same.
  • the two-cylinder rotary compressor technology and the refrigerant injection technology are often used, but the manufacturing cost of the two-cylinder compressor is high, and the energy efficiency improvement is not obvious. Low cost performance.
  • 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 compressor that has high compression efficiency and low cost.
  • the present invention also proposes a refrigeration apparatus having the above compressor.
  • a compressor includes: a cylinder, at least one piston, at least one sliding piece, a first blocking member, and a second blocking member, wherein the cylinder is provided with a cylinder chamber and a vane groove,
  • the piston chamber is provided with the eccentrically rotating piston, the cylinder chamber defining a first working chamber through a corresponding piston and a corresponding sliding piece, the first working chamber including a compression chamber and a suction a cavity having a first exhaust port, the suction cavity having a first intake port, and the first blocking member and the second blocking member are respectively disposed on the cylinder to block
  • Two sides of the sliding groove define a second working cavity, the second working cavity is provided with a second suction port and a second exhaust port, and the sliding piece is reciprocally disposed on the sliding piece
  • the inside of the groove is such that the internal pressure of the second working chamber is variable, wherein the height of the cylinder is H, the eccentricity of the crankshaft is e, the width of the sliding groove is L, and
  • the compressor according to the embodiment of the invention not only has better compression performance and compression efficiency, but also has higher work reliability and stability, and provides more convenience for integrating other functions, and has low production cost and high performance. Value for money.
  • an angle ⁇ between the slider slot and the first air inlet wherein 20° ⁇ ⁇ ⁇ 40°.
  • the slider slot has a width L>1.1e.
  • the side wall of the piston is formed with an arcuate groove
  • the head of the slider has a circular arc portion adapted to the arcuate groove
  • wrap angle of the outer wall of the circular arc portion is ⁇ , where ⁇ 180°.
  • the head of the sliding piece has a relief recess connected to an outer end of the circular arc portion.
  • the number of the avoidance recesses is two and symmetrically distributed on both sides of the arc portion.
  • the relief recess is a circular arc surface or is composed of a plurality of planes.
  • the diameter of the circular arc portion is smaller than the thickness of the sliding piece.
  • a refrigeration apparatus includes the compressor of the above embodiment.
  • FIG. 1 is a cross-sectional view of a cylinder, a piston, and a slider of a compressor according to an embodiment of the present invention
  • FIG. 2 is a schematic view of a slider of a compressor according to an embodiment of the present invention.
  • Figure 3 is another schematic view of a slider of a compressor in accordance with an embodiment of the present invention.
  • FIG. 4 is a schematic view of a compressor in accordance with an embodiment of the present invention.
  • a first working chamber 41 an air suction chamber 411, a compression chamber 412, a first air inlet 4111, a first air outlet 4121,
  • the second working chamber 51, the second suction port 511, and the second exhaust port 512 are identical to each other.
  • a compressor 100 according to an embodiment of the present invention will be described below with reference to FIGS. 1 through 4.
  • the compressor 100 includes a cylinder 10, at least one piston 20, at least one sliding piece 30, a first blocking member (not shown), and a second blocking member (not shown). .
  • a cylinder chamber and a vane slot are disposed in the cylinder 10, and an eccentrically rotating piston 20 is disposed in the cylinder chamber.
  • the cylinder chamber defines a first working chamber 41 through a corresponding piston 20 and a corresponding sliding plate 30.
  • the first working chamber 41 includes The compression chamber 411 and the suction chamber 412 have a first exhaust port 4121, and the suction chamber 411 has a first intake port 4111.
  • the first blocking member and the second blocking member are respectively disposed on the cylinder 10 to block the two sides of the sliding slot to define the second working chamber 51, and the second working chamber 51 is provided with the second suction opening 511 and the first
  • the two exhaust ports 512 are reciprocally disposed in the slider slots to make the internal pressure of the second working chamber 51 variable.
  • the compressor 100 of the embodiment of the present invention by using a double-cavity cylinder having two working chambers, the refrigerant in the second working chamber 51 defined by the sliding groove and the first blocking member and the second blocking member can be Compression, so that the refrigerant can be independently compressed by the second working chamber 51 while realizing the conventional compression of the refrigerant by the first working chamber 41, thereby improving the energy efficiency of the compressor 100, facilitating the processing and assembly of the compressor 100, and improving compression.
  • the production efficiency of the machine 100 can simultaneously reduce the manufacturing cost of the compressor 100.
  • the height of the cylinder 10 is H
  • the eccentricity of the crankshaft is e
  • the width of the sliding groove is L
  • the volume of the compression chamber 412 is V when the piston 20 has just rotated through the first suction port 4111, 5% ⁇ 2L* H*e/V ⁇ 80%.
  • the compressor 100 not only has better compression performance and compression efficiency, but also has higher operational reliability and stability, and provides more convenience for integrating other functions.
  • the direction “inner” can be understood as a direction toward the center of the cylinder 10, and the opposite direction is defined as “outer”, that is, a direction away from the center of the cylinder 10.
  • the cylinder 10 is formed with a first working chamber 41 and a vane slot.
  • the vane slot can extend in the inner and outer directions of the cylinder 10, the piston 20 is disposed in the first working chamber 41, and the piston 20 is along the first working chamber 41.
  • the inner wall is rotatable, and the sliding piece 30 is movably disposed in the sliding groove.
  • the portion of the sliding groove located at the end of the sliding piece 30 ie, the end of the sliding piece 30 away from the center of the cylinder 10) may be formed as the second working chamber 51.
  • the first blocking member may be an inhalation valve
  • the second blocking member may be an exhaust valve.
  • the refrigerant compression process of the second working chamber 51 will be briefly described below.
  • the piston is in the process of 0° ⁇ 180°
  • the second working chamber 51 is in the suction stroke
  • the sliding piece 30 moves inward
  • the internal volume of the second working chamber 51 gradually becomes larger
  • the refrigerant pushes the suction valve into the second.
  • the working chamber 51 when the piston is in the process of 180° ⁇ 360°, the second working chamber 51 is in the compression stroke, and the sliding piece 30 moves outward.
  • the internal volume of the second working chamber 51 gradually becomes smaller, and the sliding piece 30 starts to be opposite.
  • the refrigerant in the second working chamber 51 is independently compressed.
  • the exhaust valve is pushed open, and the compressed refrigerant is discharged, thereby achieving the double-cavity cylinder. Independent compression of the refrigerant.
  • the angle between the slider groove and the first suction port 4111 is ⁇ , where 20° ⁇ ⁇ ⁇ 40°.
  • the angle ⁇ between the vane groove disposed on the cylinder 10 and the first intake port 4111 specifically represents the position at which the vane groove is disposed on the cylinder 10.
  • the suction chamber 411 of the first working chamber 41 and the compression chamber 412 are not coordinated during operation, and the working efficiency of the first working chamber 41 is lowered, and the angle ⁇ is too small, which may result in the second work.
  • the arrangement space of the cavity 51 is too small to be designed and produced, that is, the angle ⁇ between the slider slot and the first suction port 4111 is excessively lowered to reduce the working efficiency of the first working chamber 41, and the slider slot and the first If the angle ⁇ of one suction port 4111 is too small, the production cost of the second working chamber is high during the production process. Thereby, the angle ⁇ between the moderate sliding groove and the first suction port 4111 is set, which not only ensures the working efficiency of the first working chamber 41, but also reduces the production cost and the design and development cost of the compressor 100.
  • the width L of the sliding groove is >1.1e
  • the width of the sliding groove is not less than 1.1 times the eccentricity
  • the piston 20 is eccentrically rotated while the sliding plate 30 is along with the piston 20.
  • the reciprocating motion is performed in the slider groove, and the larger the width of the slider groove, the larger the volume of the second working chamber 51, and the larger the thickness of the slider 30 disposed in the slider groove.
  • the side wall of the piston 20 is formed with an arcuate groove 21, and the head of the slider 30 has a circular arc portion 31 adapted to the arcuate groove 21. Therefore, after the head of the sliding piece 30 is inserted into the curved groove 21, the sliding piece 30 can swing to the left and right with respect to the circular arc portion 31, thereby improving the compression efficiency of the second working chamber 51, and the compression effect of the compressor 100 is better. .
  • the wrap angle of the outer wall of the circular arc portion 31 is ⁇ , where ⁇ ⁇ 180°.
  • the outer wall of the circular arc portion 31 adopts the above-mentioned wrap angle to make the connection between the piston 20 and the sliding plate 30 more tight, and the sliding plate 30 does not escape from the arcuate groove 21, so that the work of the second working chamber 51 is more stable, and
  • the sliding piece 30 swinging at an angle and the head of the sliding piece 30 inserted into the curved groove 21 make the relative airtightness between the suction chamber 411 of the compressor 100 and the compression chamber 412 better, so that the first working chamber 41 Mechanically more efficient.
  • the head portion of the slider 30 has a relief recess 32 that is connected to the outer end of the circular arc portion 31.
  • the relief recess 32 By providing the relief recess 32, the slider 30 does not interfere with each other when it is swung left and right with respect to the piston 20.
  • the number of the avoidance recesses 32 is two and symmetrically distributed on both sides of the circular arc portion 31.
  • the relief recess 32 is symmetrically disposed on both sides of the circular arc portion 31 so that the slide 30 and the piston 20 do not interfere with each other regardless of whether the piston 20 rotates clockwise or counterclockwise. Thereby, the operation of the compressor 100 is made more stable.
  • the relief recess 32 is a circular arc surface or consists of a plurality of planes.
  • the diameter of the circular arc portion is smaller than the thickness of the sliding piece 30.
  • the diameter of the circular arc portion and the curved groove 21 the more the relative friction Small, so that the frictional power consumption is smaller, so that the second working chamber 51 is more mechanically efficient, and the compressor 100 operates at a lower working loss.
  • the refrigeration apparatus includes the compressor 100 of the above embodiment (see Fig. 4).
  • the refrigeration apparatus according to the embodiment of the present invention can meet the requirements of high cost performance and has the advantages of simple manufacture, safety and reliability.
  • first and second may include one or more of the features, either explicitly or implicitly.
  • a plurality means two or more unless otherwise stated.

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

Abstract

一种压缩机(100)及制冷设备，压缩机(100)包括：气缸(10)、活塞(20)、滑片(30)、第一封堵件和第二封堵件。气缸(10)内设有气缸腔和滑片槽，气缸腔内设有偏心转动的活塞(20)，气缸腔通过活塞(20)和滑片(30)限定出第一工作腔(41)，第一工作腔(41)包括压缩腔(411)和吸气腔(412)，压缩腔(411)具有第一排气口(4121)，吸气腔(412)具有第一吸气口(4111)。第一封堵件和第二封堵件分别设在气缸(10)上以封堵滑片槽的两侧以限定出第二工作腔(51)，第二工作腔(51)设有第二吸气口(511)和第二排气口(512)，滑片(30)可往复运动的设于滑片槽内以使第二工作腔(51)的内压可变；气缸(10)的高度为H，曲轴的偏心距为e，滑片槽的宽度为L，在活塞(20)刚转过第一吸气口(4111)时压缩腔(411)的容积为V，其中，5％≤2L*H*e/V≤80％。

Description

压缩机以及具有它的制冷设备
相关申请的交叉引用
本申请要求广东美芝制冷设备有限公司于2017年7月31日提交的、中国专利申请号“201720948108.2”、发明名称为“压缩机以及具有它的制冷设备”的优先权。
技术领域
本发明涉及压缩机技术领域，具体而言，涉及一种压缩机以及具有它的制冷设备。
背景技术
相关技术中，为了提高空调器的能效与特殊工况下的工作能力，多采用双缸旋转压缩机技术以及冷媒喷射技术，但是双缸压缩机的制造成本较高，并且能效提升并不明显，性价比低。
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，本发明提出一种压缩效率高、成本较低的压缩机。
本发明还提出了一种具有上述压缩机的制冷设备。
根据本发明第一方面的实施例的压缩机包括：气缸、至少一个活塞、至少一个滑片、第一封堵件和第二封堵件，所述气缸内设有气缸腔和滑片槽，所述气缸腔内设有偏心转动的所述活塞，所述气缸腔通过相应的所述活塞和相应的所述滑片限定出第一工作腔，所述第一工作腔包括压缩腔和吸气腔，所述压缩腔具有第一排气口，所述吸气腔具有第一吸气口，所述第一封堵件和所述第二封堵件分别设在所述气缸上以封堵所述滑片槽的两侧以限定出第二工作腔，所述第二工作腔设有第二吸气口和第二排气口，所述滑片可往复运动的设于所述滑片槽内以使得所述第二工作腔的内压可变，其中，所述气缸的高度为H，所述曲轴的偏心距为e，所述滑片槽的宽度为L，在活塞刚转过所述第一吸气口时所述压缩腔的容积为V，其中，5％≤2L*H*e/V≤80％。
根据本发明实施例的压缩机，不仅具有较好的压缩性能和压缩效率，而且工作可靠性和稳定性更高，还为集成其它功能提供了更多便利，而且生产成本低，具有较高的性价比。
根据本发明的一些实施例，所述滑片槽与所述第一吸气口的夹角θ，其中20°≤θ≤40°。
可选地，所述滑片槽的宽度L＞1.1e。
根据本发明的一些实施例，所述活塞的侧壁形成有弧形凹槽，所述滑片的头部具有与所述弧形凹槽相适配的圆弧部。
进一步地，所述圆弧部的外壁的包角为α，其中，α＜180°。
可选地，所述滑片的头部具有连接在所述圆弧部的外端的避让凹部。
根据本发明的一个具体的实施例，所述避让凹部的个数为两个且对称分布在所述圆弧部的两侧。
进一步地，所述避让凹部为一个圆弧面或者由多个平面组成。
可选地，所述圆弧部的直径小于所述滑片的厚度。
根据本发明第二方面实施例的制冷设备包括上述实施例的压缩机。
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压缩机的气缸、活塞以及滑片的剖视图；
图2是根据本发明实施例的压缩机的滑片的示意图；
图3是根据本发明实施例的压缩机的滑片的另一个示意图；
图4是根据本发明实施例的压缩机的示意图。
附图标记：
压缩机100，
气缸10，
活塞20，弧形凹槽21，
滑片30，圆弧部31，避让凹部32，
第一工作腔41，吸气腔411，压缩腔412，第一吸气口4111，第一排气口4121，
第二工作腔51，第二吸气口511，第二排气口512。
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至图4描述根据本发明实施例的压缩机100。
如图1所示，压缩机100包括：气缸10、至少一个活塞20、至少一个滑片30、第一封堵件(图中未示出)和第二封堵件(图中未示出)。
气缸10内设有气缸腔和滑片槽，气缸腔内设有偏心转动的活塞20，气缸腔通过相应的活塞20和相应的滑片30限定出第一工作腔41，第一工作腔41包括压缩腔411和吸气腔412，压缩腔412具有第一排气口4121，吸气腔411具有第一吸气口4111。
第一封堵件和第二封堵件分别设在气缸10上以封堵滑片槽的两侧以限定出第二工作腔51，第二工作腔51设有第二吸气口511和第二排气口512，滑片30可往复运动的设于滑片槽内以使得第二工作腔51的内压可变。
根据本发明实施例的压缩机100，通过采用具有两个工作腔的双腔气缸，使滑片槽与第一封堵件、第二封堵件限定的第二工作腔51内的冷媒可被压缩，从而在实现第一工作腔41对冷媒的常规压缩的同时能够借助第二工作腔51对冷媒进行独立压缩，进而提高了压缩机100的能效，便于压缩机100的加工和装配，提高压缩机100的生产效率，同时能够降低压缩机100的制造成本。
其中，气缸10的高度为H，曲轴的偏心距为e，滑片槽的宽度为L，在活塞20刚转过第一吸气口4111时压缩腔412的容积为V，5％≤2L*H*e/V≤80％。由此，该压缩机100不仅具有较好的压缩性能和压缩效率，而且工作可靠性和稳定性更高，还为集成其它功能提供了更多便利。
需要说明的是，方向“内”可以理解为朝向气缸10中心的方向，其相反方向被定义为“外”，即远离气缸10中心的方向。
具体地，气缸10上形成有第一工作腔41和滑片槽，滑片槽可以沿气缸10的内外方向延伸，活塞20设在第一工作腔41内，且活塞20沿第一工作腔41的内壁可转动，滑片30可活动地设在滑片槽内，滑片槽的位于滑片30尾部(即滑片30的远离气缸10中心的一端)的部分可以形成为第二工作腔51，第一封堵件可以是吸气阀，第二封堵件可以是排气阀。
下面简述第二工作腔51的冷媒压缩过程。当活塞由0°→180°过程时，第二工作腔51处于吸气行程，滑片30向内运动，第二工作腔51的内部容积逐渐变大，冷媒会推开吸气阀进入第二工作腔51，当活塞由180°→360°过程时，第二工作腔51处于压缩行程，滑片30向外运动，此时第二工作腔51的内部容积逐渐变小，滑片30开始对第二工作腔51内的冷媒进行独立压缩，当第二工作腔51内的压力达到压缩机100壳体内压力时排气阀被推开，压缩后的冷媒被排出，由此通过双腔气缸实现了对冷媒的独立压缩。
值得注意的是，上述的0°→180°、180°→360°的吸气、排气行程只是针对第二工作腔51的，第一工作腔41什么时候吸气、什么时候排气的角度则可能不是上述值。
如图2所示，滑片槽与第一吸气口4111的夹角θ，其中20°≤θ≤40°。
具体而言，布置在气缸10上的滑片槽与第一吸气口4111之间的夹角θ具体体现的是滑片槽在气缸10上布置的位置。当夹角θ过大时会导致第一工作腔41的吸气腔411与压缩腔412在工作时不协调，降低第一工作腔41的工作效率，夹角θ过小，会导致第二工作腔51的布置空间太小，难于设计以及生产，也就是说，滑片槽与第一吸气口4111之间的夹角θ过大会降低第一工作腔41的工作效率，滑片槽与第一吸气口4111的夹角θ过小，那么生产过程中，第二工作腔的生产成本较高。由此，设置适中的滑片槽与第一吸气口4111之间的夹角θ，不仅可以保证第一工作腔41的工作效率，还能降低生产成本以及压缩机100的设计研发成本。
根据本发明的一个具体的实施例，滑片槽的宽度L＞1.1e，滑片槽的宽度不少于1.1倍的偏心距，活塞20做偏心旋转运动的同时滑片30随着活塞20在滑片槽中做往复运动，滑片槽的宽度越大那么第二工作腔51的容积越大，并且设置在滑片槽中的滑片30的厚度也就越大。由此，不仅使第二工作腔51单位时间内所能压缩的冷媒更多，还使压缩机100的工作稳定性更高。
参照图3所示，活塞20的侧壁形成有弧形凹槽21，滑片30的头部具有与弧形凹槽21相适配的圆弧部31。由此，使滑片30的头部插入弧形凹槽21后，滑片30可以相对圆弧部31左右摆动，进而提高第二工作腔51的压缩效率，使压缩机100的压缩效果更好。
进一步地，圆弧部31的外壁的包角为α，其中，α＜180°。这样，圆弧部31的外壁采用上述包角使活塞20与滑片30的连接更加紧密，滑片30不会从弧形凹槽21中脱出使第二工作腔51的工作更加稳定，且能够摆动一定角度的滑片30、插入弧形凹槽21内的滑片30的头部使压缩机100的吸气腔411与压缩腔412之间的相对密闭性更好，使第一工作腔41的机械效率更高。
如图2和图3所示，滑片30的头部具有连接在圆弧部31的外端的避让凹部32。通过设置避让凹部32，使滑片30相对活塞20左右摆动时不会互相干涉。
根据本发明的一个具体的实施例，避让凹部32的个数为两个且对称分布在圆弧部31的两侧。这样，在圆弧部31的两侧对称设置避让凹部32，使无论是活塞20顺时针转动还是逆时针转动，滑片30与活塞20之间都不会相互干涉。由此，使压缩机100工作更加地稳定。
根据图2和图3所示的具体的实施例，避让凹部32为一个圆弧面或者由多个平面组成。
可选地，圆弧部的直径小于滑片30的厚度，滑片30的头部在弧形凹槽21内摆动时，直径越小的圆弧部与弧形凹槽21的相对摩擦就越小，从而摩擦功耗就越小，进而使第二工作腔51机械效率更高，压缩机100工作时的工损更低。
根据本发明第二方面实施例的制冷设备包括上述实施例的压缩机100(参见图4)。
根据本发明实施例的制冷设备，可以满足高性价比的要求，并且具有制造简单、安全可靠的优点。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“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结构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，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. 一种压缩机，其特征在于，包括：
    气缸，所述气缸内设有气缸腔和滑片槽；
    至少一个活塞，所述气缸腔内设有偏心转动的所述活塞；
    至少一个滑片，所述气缸腔通过相应的所述活塞和相应的所述滑片限定出第一工作腔，所述第一工作腔包括压缩腔和吸气腔，所述压缩腔具有第一排气口，所述吸气腔具有第一吸气口；
    第一封堵件和第二封堵件，所述第一封堵件和所述第二封堵件分别设在所述气缸上以封堵所述滑片槽的两侧以限定出第二工作腔，所述第二工作腔设有第二吸气口和第二排气口，所述滑片可往复运动的设于所述滑片槽内以使得所述第二工作腔的内压可变；
    其中，所述气缸的高度为H，所述曲轴的偏心距为e，所述滑片槽的宽度为L，在活塞刚转过所述第一吸气口时所述压缩腔的容积为V，其中，5％≤2L*H*e/V≤80％。
  2. 根据权利要求1所述的压缩机，其特征在于，所述滑片槽与所述第一吸气口的夹角θ，其中20°≤θ≤40°。
  3. 根据权利要求1或2所述的压缩机，其特征在于，所述滑片槽的宽度L＞1.1e。
  4. 根据权利要求1-3中任一项所述的压缩机，其特征在于，所述活塞的侧壁形成有弧形凹槽，所述滑片的头部具有与所述弧形凹槽相适配的圆弧部。
  5. 根据权利要求4所述的压缩机，其特征在于，所述圆弧部的外壁的包角为α，其中，α＜180°。
  6. 根据权利要求4或5所述的压缩机，其特征在于，所述滑片的头部具有连接在所述圆弧部的外端的避让凹部。
  7. 根据权利要求6所述的压缩机，其特征在于，所述避让凹部的个数为两个且对称分布在所述圆弧部的两侧。
  8. 根据权利要求6-7中任一项所述的压缩机，其特征在于，所述避让凹部为一个圆弧面或者由多个平面组成。
  9. 根据权利要求4-8中任一项所述的压缩机，其特征在于，所述圆弧部的直径小于所述滑片的厚度。
  10. 一种制冷设备，其特征在于，包括如权利要求1-9中任一项所述的压缩机。
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