WO2020042443A1 - 压缩机的主轴、压缩机和空调器 - Google Patents

压缩机的主轴、压缩机和空调器 Download PDF

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Publication number
WO2020042443A1
WO2020042443A1 PCT/CN2018/121456 CN2018121456W WO2020042443A1 WO 2020042443 A1 WO2020042443 A1 WO 2020042443A1 CN 2018121456 W CN2018121456 W CN 2018121456W WO 2020042443 A1 WO2020042443 A1 WO 2020042443A1
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WO
WIPO (PCT)
Prior art keywords
main shaft
pressure
compressor
groove
exhaust
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/CN2018/121456
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English (en)
French (fr)
Inventor
吴飞
万鹏凯
史进飞
孙文娇
罗发游
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Publication of WO2020042443A1 publication Critical patent/WO2020042443A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the invention relates to the technical field of compressor manufacturing, in particular to a compressor main shaft, a compressor and an air conditioner.
  • the sliding vane compressor in the prior art generally includes a cylinder, a main shaft, and a sliding vane.
  • the main shaft rotates in the cylinder and drives the sliding vane to rotate.
  • the sliding vane protrudes from the sliding vane groove under the action of centrifugal force and communicates with the interior of the cylinder
  • the peripheral wall abuts and divides the space in the cylinder into multiple independent compression chambers.
  • the volume of some of the compression chambers decreases with the rotation of the main shaft, thereby compressing the gas and increasing the pressure of the gas through the exhaust port.
  • the volume of the other part of the compression chamber is increased to complete the suction of the gas.
  • this part of the gas is excessively compressed, and it also causes the exhaust tail of the sliding blade head.
  • the pressure of the cavity is greater than the pressure of the back pressure of the sliding blade at the tail of the sliding blade, which causes the sliding blade to detach from the inner peripheral wall of the cylinder, which affects the reliability of the compressor.
  • the main purpose of the present invention is to provide a compressor main shaft, a compressor, and an air conditioner, so as to solve the problem that some gas in the compressor in the prior art is over-compressed, thereby reducing the service life of the compressor and using the compressor reliably. Sexual problems.
  • a main shaft of a compressor includes a main shaft body, and an outer peripheral wall of the main shaft body is provided with a sliding vane groove and a pressure exhaust groove.
  • a connected exhaust pressure groove and a sliding blade groove form a group of exhaust units, and a plurality of groups of exhaust units are arranged at intervals around the circumferential direction of the main shaft body.
  • the exhaust groove extends around the circumferential direction of the main shaft body, and has an inlet end in communication with the sliding blade groove in an extension direction thereof and an outlet end away from the sliding blade groove in a direction opposite to the rotation direction of the main shaft body.
  • the pressure relief groove is parallel to the radial plane of the main shaft body; or the pressure relief groove and the radial plane of the main shaft body are arranged at an angle.
  • one pressure-relief groove there is one pressure-relief groove, and one pressure-relief groove is located in an axial middle portion of the main shaft body; or, there are a plurality of pressure-relief grooves, and the plurality of pressure-relief grooves are arranged at intervals along the axial direction of the main shaft body.
  • the depth of the pressure-relief groove in the radial direction of the main shaft body is 0.01 mm or more and 3 mm or less.
  • the width of the pressure-relief groove in the axial direction of the main shaft body is 0.1 mm or more and 3 mm or less.
  • a compressor including: a cylinder having a receiving cavity; a main shaft, the main shaft being the above-mentioned main shaft, the main shaft being eccentrically assembled with the air cylinder; Inside.
  • the compressor further includes two flanges, the flanges are sleeved on the main shaft and are in contact with the two end surfaces of the cylinder, respectively.
  • the flanges are provided with an air inlet and an air outlet that communicate with the receiving cavity.
  • the side wall of the cylinder is provided with an intake port and an exhaust port which communicate with the receiving cavity.
  • the exhaust groove of the main shaft is used to communicate the exhaust tail cavity and the low-pressure cavity.
  • the air inlet is in communication with the low-pressure cavity.
  • an air conditioner including the above-mentioned compressor.
  • a pressure-relief groove communicating with the sliding blade groove is opened on the outer peripheral wall of the main shaft body, and the structure of the main shaft of the compressor is optimized, thereby improving the performance of the compressor to which the main shaft of the compressor of the present application is applied. Service life and service reliability.
  • the exhaust pressure groove can communicate the exhaust tail chamber with the low-pressure chamber, so that the remaining gas in the exhaust tail chamber can be
  • the exhaust groove enters the low-pressure cavity, which effectively prevents the remaining gas in the exhaust tail cavity from being over-compressed, thereby increasing the service life of the compressor, ensuring that the sliding blade always abuts against the inner peripheral wall of the cylinder, and improves To improve the reliability of the compressor.
  • FIG. 1 shows an exploded structure diagram of a compressor according to an alternative embodiment of the present invention
  • FIG. 2 shows a partial structural schematic diagram of the compressor of FIG. 1 after assembly
  • FIG. 3 is a schematic structural diagram of a main shaft of the compressor of FIG. 1;
  • FIG. 4 is a schematic cross-sectional view of the main shaft of FIG. 3.
  • the present invention provides a compressor main shaft, a compressor, and an air conditioner .
  • the compressor includes the above-mentioned and the following main shafts
  • the air conditioner includes the above-mentioned and the following compressors.
  • the compressor includes a cylinder 100, a main shaft 200, and a sliding plate 300.
  • the cylinder has a receiving chamber 101.
  • the main shaft 200 is the above-mentioned and the following main shafts.
  • the main shaft 200 is eccentrically assembled with the air cylinder 100.
  • the main shaft body 10 is located in the accommodating cavity 101, and a part of the outer wall surface of the main shaft body 10 abuts a part of the inner peripheral wall of the air cylinder 100.
  • the sliding plate 300 is installed in the sliding plate groove 11 of the main shaft 200.
  • the sliding plate 300 rotates with the main shaft 200.
  • the sliding plate 300 protrudes from the sliding plate groove 11 and always abuts against the inner peripheral wall of the cylinder 100.
  • the compressor further includes two flanges 400.
  • the flange 400 is sleeved on the main shaft 200 and abuts the two end surfaces of the cylinder 100 respectively.
  • the flange 400 is provided with a receiving cavity.
  • An air inlet 401 and an air outlet 402 are communicated with 101.
  • the compressor is an axial suction and exhaust compressor, and the main shaft of the compressor provided in this application can be applied to an axial suction and exhaust compressor .
  • a side wall of the cylinder 100 is provided with an air inlet 401 and an air outlet 402 that communicate with the receiving cavity 101.
  • the compressor is a radial suction and exhaust compressor.
  • the main shaft of the compressor provided in this application can be applied to a radial suction and exhaust compressor.
  • the compressor further includes a cover plate 800, which is sleeved on the main shaft 200 and abuts against the surface of the flange.
  • the main shaft 200 includes a main shaft body 10 and two connecting rod sections 20 located at both ends of the main shaft body 10.
  • the cross-sectional areas of the two connecting rod sections 20 are smaller than the cross-sectional area of the main shaft body 10.
  • the two connecting rod sections 20 are used for assembling with the flange 400. After the compressor is assembled, the main shaft body 10 is located in the receiving cavity 101 of the air cylinder 100.
  • the outer peripheral wall of the main shaft body 10 is provided with a sliding blade groove 11 and a pressure exhaust groove 12 that communicate with each other.
  • the present application provides a pressure relief groove 12 on the outer peripheral wall of the main shaft body 10 which communicates with the sliding blade groove 11 to optimize the structure of the main shaft 200 of the compressor, thereby improving the performance of the compressor to which the main shaft 200 of the compressor of the present application is applied. Service life and service reliability.
  • the exhaust pressure groove 12 can communicate the exhaust tail chamber 500 with the low-pressure chamber 600, so that the exhaust tail The remaining gas in the cavity 500 can enter the low-pressure cavity 600 through the pressure-relief groove 12, thereby effectively preventing the remaining gas in the exhaust tail cavity 500 from being excessively compressed, thereby improving the service life of the compressor and ensuring the sliding vane. 300 is always in contact with the inner peripheral wall of the cylinder 100, which improves the reliability of the compressor.
  • the compressor has a plurality of sliding blades 300, and each sliding blade groove 11 is equipped with a sliding blade 300.
  • the multiple sliding blades 300 rotate with the main shaft 200 and divide the receiving cavity 101 in the cylinder 100 into a plurality of independent Compression chamber.
  • the other sliding piece 300 of the rotating part passes through the abutting position of the main shaft body 10 and the cylinder 100; the side wall surface of the sliding piece 300 near the abutting position, the inner peripheral wall of the cylinder 100, and the outer wall surface of the main shaft body 10 rotates through the exhaust port 402
  • a low-pressure cavity 600 is formed between the exhaust tail cavity 500 and the side wall surface of the sliding sheet 300 which is turned to the abutment position near the abutment position, the inner peripheral wall of the cylinder 100 and the outer wall surface of the main shaft body 10.
  • the air port 401 is in communication with the low-pressure chamber 600.
  • the plurality of sliding plates 300 rotates with the main shaft 200, and the volume of the low-pressure chamber 600 gradually increases to complete the inhalation of gas. Accordingly, the volume of the exhaust tail chamber 500 gradually decreases. Excess gas causes excessive compression.
  • Exhaust pressure tank 12 connects exhaust tail chamber 500 and low pressure chamber 600. Exhaust gas in exhaust tail chamber 500 can enter low pressure chamber 600 through exhaust pressure tank 12 to avoid exhaust tail chamber 500.
  • the increased pressure creates a large biasing force on the side of the sliding plate 300, thereby effectively avoiding abnormal wear of the sliding plate 300, improving the service life of the compressor, and avoiding the exhaust of the head of the sliding plate 300.
  • the pressure of the air tail chamber 500 is greater than the pressure of the sliding plate back pressure chamber 700 at the tail of the sliding plate 300, which causes the sliding plate 300 to detach from the inner peripheral wall of the cylinder 100, which affects the reliability of the compressor.
  • the exhaust tail chamber 500 and the low-pressure chamber 600 can be communicated through the exhaust pressure groove 12 communicating with the sliding plate groove 11 on which the sliding plate 300 is installed.
  • an exhaust pressure groove 12 and a sliding blade groove 11 communicating with each other form a group of exhaust units, and a plurality of groups of exhaust units are arranged at intervals around the circumference of the main shaft body 10.
  • the pressure relief groove 12 extends around the circumferential direction of the main shaft body 10, and has an inlet end 121 communicating with the sliding plate groove 11 in the extension direction thereof and a direction opposite to the rotation direction of the main shaft body 10. Far from the exit end 122 of the sliding blade slot 11.
  • the pressure exhaust groove 12 is parallel to a radial plane of the main shaft body 10. In this way, it is beneficial to the processing and manufacturing of the pressure relief groove 12.
  • the pressure-relief groove 12 is disposed at an angle with the radial plane of the main shaft body 10.
  • the pressure-relief groove 12 is provided in an arc.
  • one pressure-relief groove 12 there is one pressure-relief groove 12, and one pressure-relief groove 12 is located at an axially middle portion of the main shaft body 10. In this way, it is ensured that during the rotation of the main shaft 200, the gas in the compression chamber will not leak from the pressure exhaust groove 12.
  • the plurality of pressure exhaust grooves 12 are disposed at intervals along the axial direction of the main shaft body 10. In this way, when the volume of the exhaust tail chamber 500 is large, the gas in the exhaust tail chamber 500 can be discharged to the low-pressure chamber 600 through a plurality of pressure exhaust grooves 12 at the same time, so as to prevent the gas in the exhaust tail chamber 500 from being exhausted too late.
  • a plurality of pressure-relief grooves 12 are arranged at equal intervals along the axial direction of the main shaft body 10, so that the gas in the exhaust tail chamber 500 is smoothly and smoothly discharged from the pressure-relief groove 12 to the low-pressure chamber 600.
  • a plurality of pressure-relief grooves 12 can be arranged at non-equal intervals along the axial direction of the main shaft body 10.
  • the depth ⁇ of the pressure relief groove 12 in the radial direction of the main shaft body 10 is 0.01 mm or more and 3 mm or less. If the depth ⁇ of the exhaust pressure groove 12 in the radial direction of the main shaft body 10 is too small, the residual gas in the exhaust tail chamber 500 cannot be discharged from the exhaust tail chamber 500 into the low-pressure chamber 600 in time. The depth ⁇ of the groove 12 in the radial direction of the main shaft body 10 is too large, which increases the clearance. A large number of experiments have shown that when the depth ⁇ is in the above-mentioned value range, the pressure relief effect of the pressure relief groove 12 can be ensured, and an increase in clearance can be avoided.
  • the width of the pressure relief groove 12 in the axial direction of the main shaft body 10 is greater than or equal to 0.1 mm and less than or equal to 3 mm.
  • the sliding vane grooves 11 are arranged at equal intervals around the circumferential direction of the main shaft body 10. According to the number of the sliding vane grooves 11, the arc angle ⁇ between two adjacent sliding vane grooves 11 also changes accordingly. . In the specific embodiment shown in FIG. 1 to FIG. 4 of the present application, the number of the slide grooves 11 is three.
  • the pressure exhaust groove 12 extends a certain length along the circumferential direction of the main shaft body 10, and an arc angle ⁇ is formed between the inlet end 121 and the outlet end 122 of the pressure exhaust groove 12, and the value of the arc angle ⁇ and the setting position of the exhaust port 402
  • the value of the radian included angle ⁇ is positively related to the distance between the exhaust port 402 and the abutment position of the main shaft 200 and the cylinder 100.
  • the location of the exhaust port 402 needs to meet the requirement that the sliding plate 300 rotates past the position of the exhaust port 402.
  • the volume in the exhaust tail chamber 500 should be less than 3% of the total exhaust volume.
  • the installation position is related to the working conditions. When the working conditions are heavier, that is, the pressure ratio of suction and exhaust is larger, the exhaust port 402 is closer to the abutment position between the main shaft 200 and the cylinder 100, and the inlet end 121 of the pressure exhaust groove 12 and The smaller the radian included angle ⁇ between the exit ends 122.
  • the present invention optimizes the structure of the main shaft of the compressor, and an exhaust groove 12 is provided on the main shaft body 10 to avoid exhaust tail cavity
  • the pressure in 500 is too high, which causes the sliding plate 300 to be offset, thereby avoiding abnormal wear of the sliding plate 300, preventing the sliding plate 300 from detaching from the inner peripheral wall of the cylinder 100, and avoiding the collision between the sliding plate 300 and the cylinder 100 or the sliding plate groove 11.
  • Noise thereby improving the service life and reliability of the compressor to which the spindle is applied. Accordingly, the service life and reliability of the air conditioner to which the compressor provided by the present application is applied can be improved, and the noise of the air conditioner can be reduced.
  • orientation words such as “front, back, up, down, left, right", “horizontal, vertical, vertical, horizontal”, “top, bottom” and the like indicate the orientation Or the positional relationship is usually based on the orientation or positional relationship shown in the drawings, only for the convenience of describing the present invention and simplifying the description. Unless otherwise stated, these orientation words do not indicate and imply the device or element referred to. It must have a specific orientation or be constructed and operated in a specific orientation, so it cannot be understood as a limitation on the scope of protection of the present invention; the orientation words “inside and outside” refer to the inside and outside relative to the outline of each component itself.
  • spatially relative terms such as “above”, “above”, “above”, “above”, etc. can be used here to describe as shown in the figure Shows the spatial position relationship between one device or feature and other devices or features. It should be understood that spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation of the device as described in the figures. For example, if a device in the figure is turned over, devices described as “above” or “above” other devices or constructions will be positioned “below the other devices or constructions” or “below” Other devices or constructs. " Thus, the exemplary term “above” may include both directions “above” and “below”. The device can also be positioned in other different ways (rotated 90 degrees or at other orientations), and the relative description of space used here is explained accordingly.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

一种压缩机的主轴（200）、压缩机和空调器，其中，压缩机的主轴（200）包括主轴本体（10），主轴本体（10）的外周壁上开设有相连通的滑片槽（11）和排压槽（12）。通过该结构解决了压缩机存在的部分气体被过度压缩，从而导致压缩机的使用寿命降低，压缩机的使用可靠性差的问题。

Description

压缩机的主轴、压缩机和空调器 技术领域
本发明涉及压缩机制造技术领域，具体而言，涉及一种压缩机的主轴、压缩机和空调器。
背景技术
现有技术中的滑片式压缩机通常包括气缸、主轴和滑片，主轴在气缸内转动，并带动滑片转动，滑片在离心力的作用下由滑片槽中伸出并与气缸的内周壁抵接，将气缸内的空间分隔成多个独立的压缩室，一部分压缩室的体积随主轴的转动而减小，从而对气体进行压缩，使气体的压力增大后由排气口排出，另一部分压缩室的体积增大，从而完成气体的吸入。
但由于滑片式压缩机的结构的限制，无法在压缩机的整个排气阶段布置排气口，当滑片转过排气口后，滑片、主轴的外周壁和气缸的内周面之间形成密闭的排气尾腔，剩余的一部分气体无法排除，造成该部分气体被过度压缩，导致滑片的靠近排气尾腔一侧的压力增大并远大于滑片的另一侧的压力，从而在滑片的侧面上形成较大的偏置力，导致滑片的异常磨损，影响压缩机的使用寿命，同时，该部分气体被过度压缩，还会导致滑片头部的排气尾腔的压力大于滑片尾部的滑片背压腔的压力，造成滑片与气缸的内周壁脱离，影响压缩机的使用可靠性。
发明内容
本发明的主要目的在于提供一种压缩机的主轴、压缩机和空调器，以解决现有技术中的压缩机存在部分气体被过度压缩，从而导致压缩机的使用寿命降低，压缩机的使用可靠性差的问题。
为了实现上述目的，根据本发明的一个方面，提供了一种压缩机的主轴，主轴包括：主轴本体，主轴本体的外周壁上开设有相连通的滑片槽和排压槽。
进一步地，滑片槽为多个，排压槽为多个，多个排压槽一一对应地与多个滑片槽相连通。
进一步地，相连通的一个排压槽和一个滑片槽形成一组排气单元，多组排气单元绕主轴本体的周向间隔设置。
进一步地，排压槽绕主轴本体的周向延伸，且在其延伸方向上具有与滑片槽连通的入口端和沿主轴本体的转动方向的反方向远离滑片槽的出口端。
进一步地，排压槽平行于主轴本体的径向平面；或排压槽与主轴本体的径向平面呈夹角设置。
进一步地，排压槽为一个，一个排压槽位于主轴本体的轴向的中部；或，排压槽为多个，多个排压槽沿主轴本体的轴向间隔设置。
进一步地，排压槽的在主轴本体的径向方向的深度大于等于0.01mm且小于等于3mm。
进一步地，排压槽的在主轴本体的轴向方向的宽度大于等于0.1mm且小于等于3mm。
根据本发明的另一方面，提供了一种压缩机，包括：气缸，气缸具有容纳腔；主轴，主轴为上述的主轴，主轴与气缸偏心装配；滑片，滑片安装在主轴的滑片槽内。
进一步地，压缩机还包括两个法兰，法兰套设在主轴上，并分别与气缸的两个端面抵接，法兰上开设有与容纳腔连通的进气口和排气口。
进一步地，气缸的侧壁上开设有与容纳腔连通的进气口和排气口。
进一步地，当主轴转动至过度压缩位置时，主轴的排压槽用于连通排气尾腔和低压腔。
进一步地，进气口与低压腔连通。
根据本发明的又一方面，提供了一种空调器，包括上述的压缩机。
应用本发明的技术方案，在主轴本体的外周壁上开设与滑片槽相连通的排压槽，优化了压缩机的主轴的结构，从而提升了应用本申请的压缩机的主轴的压缩机的使用寿命和使用可靠性。具体来说，当压缩机的滑片转过排气口后，即主轴转动至过度压缩位置时，排压槽能够将排气尾腔与低压腔连通，使排气尾腔内的剩余气体能够通过排压槽进入低压腔内，从而有效地避免了排气尾腔内的剩余的部分气体被过度压缩，进而提升了压缩机的使用寿命，保证滑片与气缸的内周壁始终抵接，提升了压缩机的使用可靠性。
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示出了根据本发明的一种可选实施例的压缩机的分解结构示意图；
图2示出了图1的压缩机装配后的部分结构示意图；
图3示出了图1的压缩机的主轴的结构示意图；
图4示出了图3的主轴的剖视结构示意图。
其中，上述附图包括以下附图标记：
100、气缸；101、容纳腔；200、主轴；10、主轴本体；11、滑片槽；12、排压槽；121、入口端；122、出口端；20、连接杆段；300、滑片；400、法兰；401、进气口；402、排气口；500、排气尾腔；600、低压腔；700、滑片背压腔；800、盖板。
具体实施方式
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅是本发明一部分实施例，而不是全部的实施例。以下对至少一个示例性实施例的描述实际上仅仅是说明性的，决不作为对本发明及其应用或使用的任何限制。基于本发明中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
为了解决现有技术中的压缩机存在部分气体被过度压缩，从而导致压缩机的使用寿命降低，压缩机的使用可靠性差的问题，本发明提供了一种压缩机的主轴、压缩机和空调器。其中，压缩机包括上述和下述的主轴，空调器包括上述和下述的压缩机。
如图1至图4所示，压缩机包括气缸100、主轴200和滑片300，气缸具有容纳腔101，主轴200为上述和下述的主轴，主轴200与气缸100偏心装配，其中，主轴200的主轴本体10位于容纳腔101内，且主轴本体10的部分外壁面与气缸100的部分内周壁抵接，滑片300安装在主轴200的滑片槽11内，滑片300随主轴200转动，滑片300由滑片槽11内伸出并始终与气缸100的内周壁抵接。
如图1和图2所示，压缩机还包括两个法兰400，法兰400套设在主轴200上，并分别与气缸100的两个端面抵接，法兰400上开设有与容纳腔101连通的进气口401和排气口402。在图1和图2示出的可选实施例中，压缩机为轴向吸气和排气的压缩机，本申请提供的压缩机的主轴能够应用于轴向吸气和排气的压缩机。
在本申请一未图示实施例中，气缸100的侧壁上开设有与容纳腔101连通的进气口401和排气口402。在本申请一未图示实施例中，压缩机为径向吸气和排气的压缩机，本申请提供的压缩机的主轴能够应用于径向吸气和排气的压缩机。
如图1所示，压缩机还包括盖板800，盖板800套设在主轴200上，并与法兰的表面抵接。
如图2和图3所示，主轴200包括主轴本体10和位于主轴本体10两端的两个连接杆段20，两个连接杆段20的横截面积均小于主轴本体10的横截面积。两个连接杆段20用于与法兰400装配，压缩机装配后主轴本体10位于气缸100的容纳腔101内。
如图2和图3所示，主轴本体10的外周壁上开设有相连通的滑片槽11和排压槽12。本申请在主轴本体10的外周壁上开设与滑片槽11相连通的排压槽12，优化了压缩机的主轴200的结构，从而提升了应用本申请的压缩机的主轴200的压缩机的使用寿命和使用可靠性。具体来说，当压缩机的滑片300转过排气口402后，即主轴200转动至过度压缩位置时，排压槽12能够将排气尾腔500与低压腔600连通，使排气尾腔500内的剩余气体能够通过排压槽12进入低压腔600内，从而有效地避免了排气尾腔500内的剩余的部分气体被过度压缩，进而提升了压缩机的使用寿命，保证滑片300与气缸100的内周壁始终抵接，提升了压缩机的使用可靠性。
如图2和图3所示，滑片槽11为多个，排压槽12为多个，多个排压槽12一一对应地与多个滑片槽11相连通。相应地，压缩机具有多个滑片300，每个滑片槽11处装配有一个滑片300，多个滑片300随主轴200转动，并将气缸100内的容纳腔101分隔成多个独立的压缩室。
当主轴200与气缸100偏心装配时，主轴本体10与气缸100之间抵接，当主轴200转动至过度压缩位置时，多个滑片300中的一个转过排气口402，与之相邻的另一个滑片300转过主轴本体10与气缸100的抵接位置；转过排气口402的滑片300的靠近抵接位置的侧壁面、气缸100的内周壁和主轴本体10的外壁面之间围成排气尾腔500，转过抵接位置的滑片300的靠近抵接位置的侧壁面、气缸100的内周壁和主轴本体10的外壁面之间形成低压腔600，其中，进气口401与低压腔600连通。
这样，多个滑片300随主轴200转动，低压腔600的体积逐渐增大，完成气体的吸入，相应地，排气尾腔500的体积逐渐减小，为避免对排气尾腔500内的剩余气体造成过度压缩，排压槽12将排气尾腔500和低压腔600连通，排气尾腔500内的剩余气体能够通过排压槽12进入低压腔600内，避免排气尾腔500内的压力增大，在滑片300的侧面上形成较大的偏置力，从而有效地避免了滑片300的异常磨损，提升了压缩机的使用寿命，同时，避免滑片300头部的排气尾腔500的压力大于滑片300尾部的滑片背压腔700的压力，造成滑片300与气缸100的内周壁脱离，影响压缩机的使用可靠性。
当每个滑片300转动至过度压缩位置时，均能够通过与该滑片300安装的滑片槽11相连通的排压槽12将排气尾腔500与低压腔600连通。
如图3所示，相连通的一个排压槽12和一个滑片槽11形成一组排气单元，多组排气单元绕主轴本体10的周向间隔设置。
如图2和图3所示，排压槽12绕主轴本体10的周向延伸，且在其延伸方向上具有与滑片槽11连通的入口端121和沿主轴本体10的转动方向的反方向远离滑片槽11的出口端122。在主轴200和气缸100装配时，注意主轴200的安装方向，保证当主轴200转动至过度压缩位置时，排气尾腔500内气体能够由排压槽12的入口端121进入，由排压槽12的出口端122排出至低压腔600。
如图2所示，排压槽12平行于主轴本体10的径向平面。这样，有利于排压槽12的加工制造。
在本申请的一个未图示的实施例中，排压槽12与主轴本体10的径向平面呈夹角设置。
在本申请的一个未图示的实施例中，排压槽12呈弧度设置。
如图2所示，排压槽12为一个，一个排压槽12位于主轴本体10的轴向的中部。这样，保证在主轴200的转动过程中，压缩室内的气体不会由排压槽12处泄漏。
在本申请的一个未图示的实施例中，排压槽12为多个，多个排压槽12沿主轴本体10的轴向间隔设置。这样，当排气尾腔500的体积较大时，排气尾腔500内气体能够同时通过多个排压槽12排出至低压腔600，避免排气尾腔500内气体来不及排出的情况发生。
可选地，多个排压槽12沿主轴本体10的轴向等间隔设置，这样，有利于排气尾腔500内气体顺利平稳地由排压槽12排出至低压腔600。当然，本领域技术人员能够知晓，可以将多个排压槽12沿主轴本体10的轴向非等间隔设置。
在本申请的一个具体实施例中，排压槽12为2个，且2个排压槽12等间隔设置。
在本申请的另一个具体实施例中，排压槽12为3个，且3个排压槽12等间隔设置。
如图3所示，排压槽12的在主轴本体10的径向方向的深度δ大于等于0.01mm且小于等于3mm。如果排压槽12的在主轴本体10的径向方向的深度δ过小，会导致排气尾腔500内的剩余气体无法及时地由排气尾腔500排出至低压腔600内，如果排压槽12的在主轴本体10的径向方向的深度δ过大，会增加余隙。经大量实验表明，当深度δ处于上述数值范围时，既能够保证排压槽12的泄压效果，又能够避免增加余隙。
可选地，排压槽12的在主轴本体10的轴向方向的宽度大于等于0.1mm且小于等于3mm。
如图4所示，滑片槽11绕主轴本体10的周向等间隔设置，根据滑片槽11数量的不同，两个相邻的滑片槽11之间的弧度夹角θ也随之改变。在本申请图1至图4示出的具体实施例中，滑片槽11的数量为3个。
排压槽12沿主轴本体10的周向延伸一定的长度，排压槽12的入口端121和出口端122之间形成弧度夹角α，弧度夹角α的数值与排气口402的设置位置有关，具体来说，弧度夹角α的数值与排气口402和主轴200与气缸100的抵接位置之间的距离呈正相关。
具体来说，排气口402的设置位置需要满足滑片300在转过排气口402的位置时，排气尾腔500内的容积要小于总排气容积的3％，排气口402的设置位置与工况有关，当工况越重，即吸排气的压比越大时，排气口402越靠近主轴200与气缸100的抵接位置，则排压槽12的入口端121和出口端122之间形成弧度夹角α越小。
如图1和图2所示，排气口402为多个。
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：本发明优化了压缩机的主轴的结构，在主轴本体10上开设有排压槽12，避免排气尾腔500内的压力过高而导致滑片300偏置，从而避免滑片300异常磨损，避免滑片300与气缸100的内周壁脱离，避免滑片300与气缸100或滑片槽11之间撞击产生噪音，通过从而提升应用该主轴的压缩机的使用寿命和使用可靠性。相应地，能够提升应用本申请提供的压缩机的空调器的使用寿命和使用可靠性，降低该空调器的使用噪音。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图 包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、操作、器件、组件和/或它们的组合。
除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、数字表达式和数值不限制本发明的范围。同时，应当明白，为了便于描述，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为授权说明书的一部分。在这里示出和讨论的所有示例中，任何具体值应被解释为仅仅是示例性的，而不是作为限制。因此，示例性实施例的其它示例可以具有不同的值。应注意到：相似的标号和字母在下面的附图中表示类似项，因此，一旦某一项在一个附图中被定义，则在随后的附图中不需要对其进行进一步讨论。
在本发明的描述中，需要理解的是，方位词如“前、后、上、下、左、右”、“横向、竖向、垂直、水平”和“顶、底”等所指示的方位或位置关系通常是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，在未作相反说明的情况下，这些方位词并不指示和暗示所指的装置或元件必须具有特定的方位或者以特定的方位构造和操作，因此不能理解为对本发明保护范围的限制；方位词“内、外”是指相对于各部件本身的轮廓的内外。
为了便于描述，在这里可以使用空间相对术语，如“在……之上”、“在……上方”、“在……上表面”、“上面的”等，用来描述如在图中所示的一个器件或特征与其他器件或特征的空间位置关系。应当理解的是，空间相对术语旨在包含除了器件在图中所描述的方位之外的在使用或操作中的不同方位。例如，如果附图中的器件被倒置，则描述为“在其他器件或构造上方”或“在其他器件或构造之上”的器件之后将被定位为“在其他器件或构造下方”或“在其他器件或构造之下”。因而，示例性术语“在……上方”可以包括“在……上方”和“在……下方”两种方位。该器件也可以其他不同方式定位(旋转90度或处于其他方位)，并且对这里所使用的空间相对描述作出相应解释。
此外，需要说明的是，使用“第一”、“第二”等词语来限定零部件，仅仅是为了便于对相应零部件进行区别，如没有另行声明，上述词语并没有特殊含义，因此不能理解为对本发明保护范围的限制。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、工作、器件、组件和/或它们的组合。
需要说明的是，本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本申请的实施方式能够以除了在这里图示或描述的那些以外的顺序实施。
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 (12)

  1. 一种压缩机的主轴，其特征在于，所述主轴包括：
    主轴本体(10)，所述主轴本体(10)的外周壁上开设有相连通的滑片槽(11)和排压槽(12)。
  2. 根据权利要求1所述的主轴，其特征在于，所述滑片槽(11)为多个，所述排压槽(12)为多个，所述多个排压槽(12)一一对应地与所述多个滑片槽(11)相连通。
  3. 根据权利要求2所述的主轴，其特征在于，相连通的一个所述排压槽(12)和一个所述滑片槽(11)形成一组排气单元，多组所述排气单元绕所述主轴本体(10)的周向间隔设置。
  4. 根据权利要求1所述的主轴，其特征在于，所述排压槽(12)绕所述主轴本体(10)的周向延伸，且在其延伸方向上具有与所述滑片槽(11)连通的入口端(121)和沿所述主轴本体(10)的转动方向的反方向远离所述滑片槽(11)的出口端(122)。
  5. 根据权利要求1所述的主轴，其特征在于，所述排压槽(12)平行于所述主轴本体(10)的径向平面；或所述排压槽(12)与所述主轴本体(10)的径向平面呈夹角设置。
  6. 根据权利要求1所述的主轴，其特征在于，
    所述排压槽(12)为一个，一个所述排压槽(12)位于所述主轴本体(10)的轴向的中部；或，
    所述排压槽(12)为多个，多个所述排压槽(12)沿所述主轴本体(10)的轴向间隔设置。
  7. 根据权利要求1所述的主轴，其特征在于，所述排压槽(12)的在所述主轴本体(10)的径向方向的深度大于等于0.01mm且小于等于3mm。
  8. 根据权利要求1所述的主轴，其特征在于，所述排压槽(12)的在所述主轴本体(10)的轴向方向的宽度大于等于0.1mm且小于等于3mm。
  9. 一种压缩机，其特征在于，包括：
    气缸(100)，所述气缸具有容纳腔(101)；
    主轴(200)，所述主轴(200)为权利要求1至7中任一项所述的主轴，所述主轴(200)与所述气缸(100)偏心装配；
    滑片(300)，所述滑片(300)安装在所述主轴(200)的滑片槽(11)内。
  10. 根据权利要求9所述的压缩机，其特征在于，所述压缩机还包括两个法兰(400)，所述法兰(400)套设在所述主轴(200)上，并分别与所述气缸(100)的两个端面抵接，所述法兰(400)上开设有与所述容纳腔(101)连通的进气口(401)和排气口(402)。
  11. 根据权利要求10所述的压缩机，其特征在于，当所述主轴(200)转动至过度压缩位置时，所述主轴(200)的排压槽(12)用于连通排气尾腔(500)和低压腔(600)。
  12. 一种空调器，其特征在于，包括权利要求9至11中任一项所述的压缩机。
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