WO2016119456A1 - 滑片式压缩机及其排气结构 - Google Patents

滑片式压缩机及其排气结构 Download PDF

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Publication number
WO2016119456A1
WO2016119456A1 PCT/CN2015/088304 CN2015088304W WO2016119456A1 WO 2016119456 A1 WO2016119456 A1 WO 2016119456A1 CN 2015088304 W CN2015088304 W CN 2015088304W WO 2016119456 A1 WO2016119456 A1 WO 2016119456A1
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Prior art keywords
exhaust
type compressor
vane type
vane
exhaust structure
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PCT/CN2015/088304
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English (en)
French (fr)
Inventor
万鹏凯
徐嘉
任丽萍
罗发游
吴飞
Original Assignee
珠海格力节能环保制冷技术研究中心有限公司
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Priority to EP15879654.0A priority Critical patent/EP3252313B1/en
Priority to US15/525,808 priority patent/US10451070B2/en
Publication of WO2016119456A1 publication Critical patent/WO2016119456A1/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
    • F04C18/344—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 inner member
    • F04C18/3441—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 inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04C18/344—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 inner 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
    • F04C2240/20—Rotors
    • 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
    • F04C29/06—Silencing

Definitions

  • the present invention relates to the field of air conditioning, and in particular to a vane compressor and an exhaust structure thereof.
  • Fig. 1 and Fig. 2 most of the current vane type compressors adopt the exhaust side structure of the cylinder 1 side.
  • the exhaust port 2 and the exhaust valve piece are usually provided except at the end of compression.
  • an intermediate exhaust port 4 is also provided in the middle of the compression chamber 3, and an exhaust valve plate (also called a pressure relief valve) is provided to prevent over-compression in a lighter working condition.
  • an exhaust valve plate also called a pressure relief valve
  • a primary object of the present invention is to provide a vane type compressor and an exhaust structure thereof, which can reduce the production cost of the vane type compressor and reduce the exhaust loss of the vane type compressor.
  • an exhaust structure of a vane type compressor comprising: a vent hole provided on a flange of a vane type compressor, and sliding The compression chamber of the cylinder of the chip compressor is connected; the flow guiding channel is arranged on the flange and penetrates the flange; the exhaust passage is arranged on the eccentric circle of the vane compressor, and the exhaust passage It is used to connect the compression chamber and the flow guiding channel with the rotation of the eccentric circle.
  • the flow guiding passage extends from the vent hole in a direction in which the refrigerant in the compression chamber is compressed.
  • the extending path of the flow guiding channel is an arc, and the convex direction of the arc is away from the central axis of the flange.
  • the width of the flow guiding channel is in the range of 2 mm to 10 mm.
  • the exhaust passage extends from the outer edge of the eccentric circle toward the axis of the eccentric circle.
  • the port of the exhaust passage located at the outer edge of the eccentric circle is close to the vane groove on the eccentric circle.
  • the exhaust passage is a exhaust notch or a through hole.
  • the cross-sectional area of the exhaust passage is in the range of 0.5 mm 2 to 1.5 mm 2 .
  • exhaust passages are plural, and the plurality of exhaust passages are disposed in one-to-one correspondence with the plurality of slide grooves of the eccentric circle for mounting the plurality of slide pieces.
  • a vane type compressor including an exhaust structure having an exhaust structure of the above-described vane type compressor is provided.
  • the compressed refrigerant in operation, can be directly discharged from the compression chamber into the exhaust hole, and the remaining refrigerant can also be discharged into the flow guiding channel through the exhaust passage, compared with the prior art.
  • the side of the cylinder is provided with the structure of the side exhaust port and the exhaust valve piece.
  • the exhaust hole of the exhaust structure of the vane type compressor of the present invention can be independently set, and is not limited by the structure of the cylinder itself, and the effective area of the exhaust gas Large, and the vane compressor does not need to overcome the stiffness of the exhaust valve itself when exhausting, the exhaust pressure is equal to the back pressure, and the exhaust loss is small, which effectively reduces the power consumption of the vane compressor and the cost of manufacturing. .
  • Figure 1 is a schematic front view showing the exhaust structure of a prior art vane type compressor
  • Figure 2 is a schematic enlarged view of the M area of Figure 1;
  • Figure 3 is a schematic front view showing the exhaust structure of the vane compressor of the present invention.
  • Figure 4 is a schematic plan view showing the upper flange of the vane compressor of the present invention.
  • Fig. 5 is a schematic perspective view showing the eccentric circle of the vane type compressor of the present invention mounted on a rotating shaft.
  • a vane compressor in accordance with an embodiment of the present invention, includes a housing (not shown), a pump body (not shown), a cylinder 50, and an upper flange 40 and a lower flange (not shown).
  • the housing encloses a mounting cavity for mounting the pump body, the cylinder and the upper and lower flanges.
  • the pump body includes a rotating shaft 70 and an eccentric circle 60 disposed on the rotating shaft 70.
  • the eccentric circle 60 is provided with a slide groove 61 for mounting the slider 80.
  • the rotating shaft 70 is disposed in the cylinder 50, the eccentric circle 60 is located in the compression chamber 51 of the cylinder 50, the sliding plate 80 is mounted in the sliding slot 61, and the cylinder 50 is fixed to the housing by the upper and lower flanges. Inside the cavity.
  • the rotating shaft 70 rotates, thereby driving the eccentric circle 60 to rotate in the compression chamber 51 to compress the refrigerant in the cylinder 50, and discharging the cylinder 50 through the exhaust structure of the vane type compressor.
  • the vane compressor exhaust structure in this embodiment includes an exhaust hole 10, a flow guiding passage 20, and an exhaust passage 30, wherein the exhaust hole 10 is disposed on a flange of the vane type compressor, which can be slippery
  • the upper flange of the chip compressor may also be a lower flange, preferably an upper flange 40, and communicate with the compression chamber 51 of the cylinder 50;
  • the flow guiding passage 20 is disposed on the flange and runs through the thickness of the flange.
  • the exhaust passage 30 is disposed on an eccentric circle 60 on the rotating shaft 70 for communicating the compression chamber 51 and the flow guiding passage 20 with the rotation of the eccentric circle 60.
  • the compressed refrigerant can be directly discharged from the compression chamber 51 to the exhaust hole 10, and the remaining refrigerant can also be discharged to the flow guiding passage 20 through the exhaust passage 30, compared to the side of the cylinder in the prior art.
  • the structure of the side exhaust port and the exhaust valve piece is provided, and the exhaust hole 10 of the exhaust structure of the vane type compressor in the embodiment can be set autonomously, and is not limited by the structure of the cylinder 50 itself, and the effective area of the exhaust gas Large, and the vane compressor does not need to overcome the rigidity of the exhaust valve piece itself when exhausting the remaining refrigerant, the exhaust pressure is equal to the back pressure, and the exhaust loss is small, which effectively reduces the power consumption and manufacturing of the vane compressor. cost.
  • the flow guiding passage 20 extends from the vent hole 10 in the direction in which the refrigerant in the compression chamber 51 is compressed, so as to facilitate the removal of the high-temperature and high-pressure refrigerant remaining in the compression chamber 51 from the compression chamber 51.
  • the extending path of the flow guiding channel 20 is an arc, and the convex direction of the arc is away from the central axis of the flange.
  • This arrangement can shorten the length of the exhaust passage 30 and reduce the energy of the vane compressor. It is convenient to make the exhaust passage 30 communicate with the compression chamber 51 and the exhaust hole 10 during the rotation of the eccentric circle 60, thereby discharging the high temperature and high pressure gas in the compression chamber 51 out of the compression chamber 51.
  • the plurality of vent holes 10 are plural, and the plurality of vent holes 10 and the flow guiding passage 20 are sequentially arranged in the direction in which the refrigerant in the compression chamber 51 is compressed, when the eccentric circle 60 is closest to the direction in which the refrigerant is compressed.
  • the flow guiding passage 20 is located between the venting opening 10 and the minimum clearance of the eccentric circle 60 and the compression chamber 51 to facilitate the exhaust.
  • the width of the flow guiding channel 20 is in the range of 2 mm to 10 mm. For example, 6mm, to ensure the smoothness of the exhaust.
  • the exhaust passage 30 in this embodiment extends from the outer edge of the eccentric circle 60 toward the axis of the eccentric circle 60, and facilitates communication with the flow guiding passage 20 when the eccentric circle 60 rotates. .
  • the port of the exhaust passage 30 at the outer edge of the eccentric circle 60 is close to the vane groove 61 of the mounting vane 80 of the eccentric circle 60, so as to facilitate the complete discharge of the refrigerant in the compression chamber 51 to the outside of the cylinder 50, exhausting After the end, the remaining gap volume is only a small clearance formed by the exhaust passage 30, and the clearance of the exhaust port is smaller than that of the side of the cylinder, which is beneficial to increase the cooling capacity of the vane compressor and reduce the power consumption of the vane compressor. Improve the energy efficiency of the vane compressor.
  • the exhaust passage 30 is a venting opening or a through hole, and has a simple structure and is easy to implement.
  • the shape can be changed according to actual conditions, and only the sliding plate 80 is required to pass through all the venting holes 10 and the flange.
  • the flow guiding channel 20 can be connected.
  • the cross-sectional area of the exhaust passage 30 in this embodiment is determined according to the remaining exhaust chamber size.
  • Preferably cross sectional area of the exhaust passage 30 is generally in the range of 0.5mm 2 to 1.5mm 2, to ensure the smoothness of the exhaust gas.
  • the exhaust passages 30 are plural, and the plurality of exhaust passages 30 are disposed in one-to-one correspondence with the plurality of sliding vanes 61 of the eccentric circle 60 for mounting the plurality of sliding vanes 80, so as to facilitate the compression quickly.
  • the high temperature and high pressure refrigerant in the chamber 51 is completely discharged to the outside of the cylinder 50, improving the performance of the vane type compressor.
  • the exhaust passage 30 When the vane type compressor is operated, the exhaust passage 30 is rotated to communicate with the flow guiding passage 20, and is connected to the back pressure exhaust gas, and the remaining gas is discharged from the exhaust passage 30 through the flow guiding passage 20.
  • the back pressure here refers to the pressure in the entire sliding vane compressor housing (a pressure formed after the compression of the vane compressor body is discharged to the housing, and the vane compressor is discharged through the exhaust pipe). ), generally lower than the pressure of the compression chamber in the pump body when the exhaust gas is exhausted (the gas in the pump body is to be discharged, and it is also necessary to overcome the self-stiffness of the valve plate.
  • the guide channel 20 is not provided with a valve piece, the remaining after passing through the vent hole 10
  • the refrigerant can be directly discharged through the flow guiding passage 20, and does not need to overcome the force of the valve piece itself, and can also avoid waste of power consumption caused by the remaining refrigerant entering the next cycle of compression).
  • the clearance volume of the structure of the vane type compressor in the embodiment is only a small clearance formed by the exhaust passage 30, and the clearance of the exhaust port is much smaller than that of the side of the cylinder, which is advantageous for improving the sliding type.
  • the compressor cooling capacity reduces the power consumption of the vane compressor and improves the energy efficiency of the vane compressor.
  • the exhaust clearance volume is small, which can effectively improve the energy efficiency of the vane compressor.

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

Abstract

一种滑片式压缩机及其排气结构。该滑片式压缩机的排气结构包括：排气孔（10），排气孔（10）设置在滑片式压缩机的法兰上，并与滑片式压缩机的气缸的压缩腔（51）连通；导流通道（20），导流通道（20）设置在法兰上并贯穿法兰；排气通道（30），排气通道（30）设置在滑片式压缩机的偏心圆（60）上，排气通道用于随偏心圆（60）的旋转将压缩腔（51）和导流通道（20）连通。该滑片式压缩机及其排气结构排气的损失小，有效降低了滑片式压缩机的功率消耗和生产制造的成本。

Description

滑片式压缩机及其排气结构 技术领域
本发明涉及空调领域，具体而言，涉及一种滑片式压缩机及其排气结构。
背景技术
参见图1和图2所示，目前滑片式压缩机大部分采用气缸1侧排气结构，为了保证不同工况的正常使用，通常除了在压缩结束位置设置排气口2及排气阀片外，还在压缩腔3中间位置开设中间排气口4，并设置排气阀片(亦称卸压阀)，以防止较轻工况时出现过压缩。同时，由于结构限制，滑片式压缩机侧排气有效面积较小，排气阻力及损失大，滑片式压缩机能效较低。此外，由于排气口2存在较大的余隙容积，其残留的气体无法从滑片式压缩机泵体内排出，随着滑片的继续转动，残留的高压气体会膨胀至后面的低压腔，又需要重复压缩，浪费滑片式压缩机功耗。
发明内容
本发明的主要目的在于提供一种滑片式压缩机及其排气结构，能够降低滑片式压缩机的生产成本，减低滑片式压缩机的排气损失。
为了实现上述目的，根据本发明的一个方面，提供了一种滑片式压缩机的排气结构，包括：排气孔，排气孔设置在滑片式压缩机的法兰上，并与滑片式压缩机的气缸的压缩腔连通；导流通道，导流通道设置在法兰上并贯穿法兰；排气通道，排气通道设置在滑片式压缩机的偏心圆上，排气通道用于随偏心圆的旋转将压缩腔和导流通道连通。
进一步地，导流通道从排气孔开始沿压缩腔中的冷媒被压缩的方向延伸。
进一步地，导流通道的延伸轨迹为弧线，弧线的凸起方向远离法兰的中心轴线。
进一步地，导流通道的宽度在2mm至10mm的范围内。
进一步地，排气通道从偏心圆的外边缘向靠近偏心圆的轴线的方向延伸。
进一步地，排气通道的位于偏心圆的外边缘的端口靠近偏心圆上的滑片槽。
进一步地，排气通道为排气缺口或通孔。
进一步地，排气通道的横截面积在0.5mm2至1.5mm2的范围内。
进一步地，排气通道为多个，多个排气通道与偏心圆的用于安装多块滑片的多个滑片槽一一对应地设置。
根据本发明的另一方面，提供了一种滑片式压缩机，包括排气结构，排气结构为上述的滑片式压缩机的排气结构。
应用本发明的技术方案，工作时，经压缩后的冷媒可以直接从压缩腔进入到排气孔后排出，剩余冷媒还可以通过排气通道进入到导流通道排出，相对于现有技术中在气缸的侧边设置侧排气口和排气阀片的结构，本发明中的滑片式压缩机的排气结构的排气孔可以自主设置，不受气缸本身结构的限制，排气有效面积大，且滑片式压缩机排气时无需克服排气阀片本身的刚度，排气压力与背压相等，排气损失小，有效降低了滑片式压缩机的功率消耗和生产制造的成本。
附图说明
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：
图1示意性示出了现有技术中的滑片式压缩机的排气结构的主视图；
图2示意性示出了图1中的M区域的放大图；
图3示意性示出了本发明的滑片式压缩机的排气结构的主视图；
图4示意性示出了本发明中的滑片式压缩机上法兰的俯视图；以及
图5示意性示出了本发明的滑片式压缩机的偏心圆安装在转轴上时的立体结构图。
其中，上述附图包括以下附图标记：
10、排气孔；20、导流通道；30、排气通道；40、上法兰；50、气缸；51、压缩腔；60、偏心圆；61、滑片槽；70、转轴；80、滑片。
具体实施方式
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。
参见图3至图5所示，根据本发明的实施例，提供了一种滑片式压缩机。该滑片式压缩机包括壳体(图中未示出)、泵体(图中未示出)、气缸50、以及上法兰40和下法兰(图中未示出)。其中，壳体围设形成安装泵体、气缸以及上下法兰的安装腔。泵体包括转轴70和设置在转轴70上的偏心圆60，偏心圆60上设置有用于安装滑片80的滑片槽61。
安装时，转轴70穿设在气缸50内，偏心圆60位于气缸50的压缩腔51内，滑片80安装在滑片槽61内，气缸50通过上下法兰固定在壳体围设形成的安装腔内。滑片式压缩机工作时，转轴70旋转，进而带动偏心圆60在压缩腔51内旋转以压缩气缸50内的冷媒，并通过滑片式压缩机的排气结构排出气缸50。
本实施例中的滑片式压缩机排气结构包括排气孔10、导流通道20以及排气通道30，其中，排气孔10设置在滑片式压缩机的法兰上，可以为滑片式压缩机的上法兰，也可以为下法兰，优选为上法兰40，并与气缸50的压缩腔51连通；导流通道20设置在法兰上并沿法兰的厚度方向贯穿法兰；排气通道30设置在转轴70上的偏心圆60上，该排气通道30用于随偏心圆60的旋转将压缩腔51和导流通道20连通。
工作时，经压缩后的冷媒可以直接从压缩腔51进入到排气孔10后排出，剩余冷媒还可以通过排气通道30进入到导流通道20排出，相对于现有技术中在气缸的侧边设置侧排气口和排气阀片的结构，本实施例中的滑片式压缩机的排气结构的排气孔10可以自主设置，不受气缸50本身结构的限制，排气有效面积大，且滑片式压缩机排出剩余冷媒时无需克服排气阀片本身的刚度，排气压力与背压相等，排气损失小，有效降低了滑片式压缩机的功率消耗和生产制造的成本。
在本实施例中，导流通道20从排气孔10开始沿压缩腔51中的冷媒被压缩的方向延伸，便于将残留在压缩腔51中的高温高压的冷媒从压缩腔51排除。
优选地，导流通道20的延伸轨迹为弧线，该弧线的凸起方向远离法兰的中心轴线，此种设置方式能够减短排气通道30的长度，降低滑片式压缩机的能耗，便于使排气通道30在偏心圆60旋转的过程中连通压缩腔51和排气孔10，进而将压缩腔51内高温高压的气体排出压缩腔51。
在本实施中，排气孔10为多个，多个排气孔10和导流通道20沿压缩腔51内的冷媒被压缩的方向依次布置，当偏心圆60最接近沿冷媒被压缩的方向上布置的最后一个排气孔10时，导流通道20位于排气孔10与偏心圆60和压缩腔51的最小间隙之间，更便于排气。
优选地，导流通道20的宽度在2mm至10mm的范围内。例如6mm，便于保证排气顺畅性。
结合图3和图5所示，本实施例中的排气通道30从偏心圆60的外边缘向靠近偏心圆60的轴线的方向延伸，当偏心圆60旋转时，便于与导流通道20连通。
优选地，排气通道30的位于偏心圆60的外边缘的端口靠近偏心圆60的安装滑片80的滑片槽61，便于将压缩腔51中的冷媒完全排放到气缸50的外部，排气结束后，其余隙容积仅为排气通道30所形成的少许余隙，较气缸侧面设置排气口余隙更小，有利于提高滑片式压缩机制冷量，降低滑片式压缩机功耗，提高滑片式压缩机能效。
优选地，排气通道30为排气缺口或通孔，结构简单，便于实现，本实施例中形状可根据实际进行更改，只要求保证滑片80在经过所有排气孔10后与法兰的导流通道20连通即可。
本实施例中的排气通道30的截面积大小根据剩余的排气腔大小决定。通常优选排气通道30的横截面积在0.5mm2至1.5mm2的范围内，保证排气顺畅性。本实施例中的排气通道30为多个，多个排气通道30与偏心圆60的用于安装多块滑片80的多个滑片槽61一一对应地设 置，便于快速地将压缩腔51中的高温高压的冷媒完全排放到气缸50外，提高滑片式压缩机的性能。
当滑片式压缩机工作时，排气通道30旋转到与导流通道20连通时，与背压排气接通，剩余气体从排气通道30经导流通道20排出。这里的背压就是指整个滑片式压缩机壳体内的压力(是从滑片式压缩机泵体压缩结束后排到壳体后形成的一个压力，其通过排气管排出滑片式压缩机)，一般低于排气时泵体内压缩腔的压力(泵体内气体要排出，还需要克服阀片的自身刚度，由于导流通道20不设有阀片，所以经过排气孔10后的剩余冷媒可以通过导流通道20直接排出，不需要克服阀片自身的力，也可以避免剩余冷媒进入下一次循环压缩所造成的功耗浪费)。
可见，本实施例中的滑片式压缩机的结构的余隙容积仅为排气通道30所形成的少许余隙，较气缸侧面设置排气口余隙小得多，有利于提高滑片式压缩机制冷量，降低滑片式压缩机功耗，提高滑片式压缩机能效。
从以上的描述中，可以看出，本发明上述的实施例实现了如下技术效果：
1、采用导流通道结构，无排气阀片，节约成本；
2、排气过程无需克服阀片自身刚度，排气损失小；
3、排气余隙容积小，可以有效提高滑片式压缩机能效。
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (10)

  1. 一种滑片式压缩机的排气结构，其特征在于，包括：
    排气孔(10)，所述排气孔(10)设置在滑片式压缩机的法兰上，并与所述滑片式压缩机的气缸(50)的压缩腔(51)连通；
    导流通道(20)，所述导流通道(20)设置在所述法兰上并贯穿所述法兰；
    排气通道(30)，所述排气通道(30)设置在所述滑片式压缩机的偏心圆(60)上，所述排气通道(30)用于随所述偏心圆(60)的旋转将所述压缩腔(51)和所述导流通道(20)连通。
  2. 根据权利要求1所述的滑片式压缩机的排气结构，其特征在于，所述导流通道(20)从所述排气孔(10)开始沿所述压缩腔(51)中的冷媒被压缩的方向延伸。
  3. 根据权利要求2所述的滑片式压缩机的排气结构，其特征在于，所述导流通道(20)的延伸轨迹为弧线，所述弧线的凸起方向远离所述法兰的中心轴线。
  4. 根据权利要求1至3中任一项所述的滑片式压缩机的排气结构，其特征在于，所述导流通道(20)的宽度在2mm至10mm的范围内。
  5. 根据权利要求1所述的滑片式压缩机的排气结构，其特征在于，所述排气通道(30)从所述偏心圆(60)的外边缘向靠近所述偏心圆(60)的轴线的方向延伸。
  6. 根据权利要求5所述的滑片式压缩机的排气结构，其特征在于，所述排气通道(30)的位于所述偏心圆(60)的外边缘的端口靠近所述偏心圆(60)上的滑片槽(61)。
  7. 根据权利要求1所述的滑片式压缩机的排气结构，其特征在于，所述排气通道(30)为排气缺口或通孔。
  8. 根据权利要求1所述的滑片式压缩机的排气结构，其特征在于，所述排气通道(30)的横截面积在0.5mm2至1.5mm2的范围内。
  9. 根据权利要求1或6所述的滑片式压缩机的排气结构，其特征在于，所述排气通道(30)为多个，所述多个排气通道(30)与所述偏心圆(60)的用于安装多块滑片(80)的多个滑片槽(61)一一对应地设置。
  10. 一种滑片式压缩机，包括排气结构，其特征在于，所述排气结构为权利要求1至9中任一项所述的滑片式压缩机的排气结构。
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