WO2020042432A1 - 泵体组件和压缩机 - Google Patents

泵体组件和压缩机 Download PDF

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Publication number
WO2020042432A1
WO2020042432A1 PCT/CN2018/120666 CN2018120666W WO2020042432A1 WO 2020042432 A1 WO2020042432 A1 WO 2020042432A1 CN 2018120666 W CN2018120666 W CN 2018120666W WO 2020042432 A1 WO2020042432 A1 WO 2020042432A1
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WO
WIPO (PCT)
Prior art keywords
oil
back pressure
groove
pressure oil
hole
Prior art date
Application number
PCT/CN2018/120666
Other languages
English (en)
French (fr)
Inventor
胡余生
魏会军
徐嘉
罗发游
万鹏凯
吴飞
张荣婷
文智明
Original Assignee
珠海格力电器股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Priority to JP2020565440A priority Critical patent/JP7329542B2/ja
Priority to EP18932135.9A priority patent/EP3786454B1/en
Priority to US17/057,730 priority patent/US11454240B2/en
Publication of WO2020042432A1 publication Critical patent/WO2020042432A1/zh

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    • 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
    • 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
    • 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
    • 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
    • F04C18/3446—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 more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • 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
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the invention relates to the technical field of compressors, in particular to a pump body assembly and a compressor.
  • sliding vane compressors Compared with other types of compressors, sliding vane compressors have the advantages of simple parts, no eccentric structure, and low torque and stable vibration. They are used in a wide range of fields. Sliding vane compressors are generally equipped with multiple sliding vanes. The operating principle is as follows: When the spindle rotates, the sliding vanes in the sliding vane groove of the spindle will make a composite movement together. The rotation of the main shaft changes continuously and cyclically to achieve compression or expansion. Therefore, the prerequisite for the normal operation of the vane compressor is that the head of the vane must always be close to the inner wall of the cylinder during the entire operating cycle. When the sliding vane compressor is running, the head of the sliding vane is always affected by the gas force in the cavity. To make the sliding vane extend out of the sliding vane groove and close to the inner wall of the cylinder, it must be ensured that the tail of the sliding vane has a greater force than the gas received by the head. The force required is sufficient back pressure on the slide.
  • the main purpose of the present invention is to provide a pump body assembly and a compressor, so as to solve the problem of insufficient back pressure of the sliding blade in the prior art.
  • a pump body assembly including: a main shaft, the main shaft having a sliding blade groove, a rear end of the sliding blade groove is a back pressure oil cavity, and the back pressure oil cavity is an oil passage;
  • the oil outlet of the back pressure oil chamber is at the top of the back pressure oil chamber, and the position of the oil inlet of the back pressure oil chamber is lower than the position of the oil outlet of the back pressure oil chamber.
  • the oil inlet of the pressure oil chamber enters the back pressure oil chamber and fills the back pressure oil chamber, and then flows out from the top of the back pressure oil chamber.
  • the main shaft also has a central oil hole extending upward from the bottom and a radial oil hole communicating with the central oil hole.
  • the central oil hole and the radial oil hole form a part of the oil passage, and the lubricant passes through the central oil hole and the radial direction.
  • the oil hole flows to the back pressure oil chamber.
  • the pump body assembly further includes a lower flange, and a lower flange is provided on a surface of the side of the lower flange facing the back pressure oil chamber.
  • the oil passage structure is such that the radial oil hole communicates with the oil inlet of the back pressure oil chamber through the lower flange oil passage structure, and the lower flange oil passage structure is part of the oil passage.
  • the lower flange oil passing structure is a lower flange back pressure oil groove provided on the lower flange, the lower flange back pressure oil groove is a stepped groove, and the stepped groove is deeper in a direction away from the main shaft.
  • the projection of the stepped groove on the lower flange is two arc-shaped structures, and the arc-shaped structure away from the main axis of the two arc-shaped structures is aligned with the back pressure oil cavity.
  • the pump body assembly further includes: an upper flange, an upper flange oil passing structure is provided on a surface of the upper flange facing the back pressure oil cavity; a bearing cylinder, the bearing cylinder has a rolling body accommodation cavity, and is disposed on The rolling body in the rolling body accommodating cavity, the oil outlet of the back pressure oil cavity communicates with the rolling body accommodating cavity through the upper flange oil passing structure, and the upper flange oil passing structure and the rolling body accommodating cavity are oil passages. portion.
  • the upper flange oil passing structure includes: an upper flange back pressure oil groove, the upper flange back pressure oil groove is communicated with the oil outlet of the back pressure oil cavity, and a radial oil hole opened along the radial direction of the upper flange, At least a part of the radial oil hole is in communication with the upper flange back pressure oil groove; the communication hole, and the rolling body accommodation cavity is in communication with the radial oil hole through the communication hole.
  • the projection of the upper flange back pressure oil groove on the upper flange is an arc structure.
  • the upper flange oil passing structure includes an oil separation groove, the upper flange back pressure oil groove communicates with the inner wall of the upper flange through the oil separation groove, there is a gap between the inner wall of the upper flange and the main shaft, and the lubrication medium passes through the upper flange back pressure The oil tank and oil separation tank flow into the gap.
  • the ratio of the cross-sectional area of the oil separation groove to the radial oil hole is 3: 7.
  • the pump body assembly further includes a lower flange, and an oil outlet groove is provided on a surface of the lower flange facing the back pressure oil cavity.
  • the bottom of the rolling body accommodation cavity communicates with the oil outlet groove, and the oil outlet groove extends to the lower method.
  • the oil tank is part of the oil passage.
  • the pump body assembly further includes a lower flange, the lower flange has an oil drain hole penetrating axially, a bottom of the rolling body accommodating cavity communicates with a top of the oil drain hole, and the oil drain hole is a part of the oil passage.
  • the pump body assembly further includes a lower flange, an oil drain communication groove is provided on a surface of the lower flange facing the back pressure oil cavity;
  • the bearing cylinder includes: an axial oil drain channel, and a bottom of the rolling body accommodation cavity
  • the oil drain communication groove communicates with the bottom of the axial oil drain channel;
  • the radial oil drain channel, the top of the axial oil drain channel communicates with the outer peripheral surface of the bearing cylinder through the radial oil drain channel, the axial oil drain channel and the radial
  • the oil discharge passage is part of the oil passage.
  • a compressor including the above-mentioned pump body assembly.
  • the pump body assembly includes a main shaft, and the main shaft has a sliding blade groove.
  • the tail end of the sliding blade groove is a back pressure oil chamber, the back pressure oil chamber is at least a part of the oil passage, and the oil is discharged from the back pressure oil chamber.
  • the port is located on the top of the back pressure oil chamber, and the position of the oil inlet of the back pressure oil chamber is lower than the position of the oil outlet of the back pressure oil chamber, so that the lubrication medium enters the back pressure oil through the oil inlet of the back pressure oil chamber.
  • the cavity is filled with the back pressure oil chamber and flows out from the top of the back pressure oil chamber.
  • the tail end of the vane groove is a back pressure oil chamber
  • a lubricating medium can be injected into the back pressure oil chamber to provide back pressure for the slide in the vane groove.
  • the position is lower than the position of the oil outlet of the back pressure oil chamber, so when the lubricating medium flows into the back pressure oil chamber, it can effectively ensure that the back pressure oil chamber is filled, thereby providing sufficient back pressure for the slide to ensure that The head of the sliding blade is always close to the inner wall of the bearing cylinder, which reduces the leakage problem of the sliding blade head and avoids the risk of the sliding blade being easily returned and detached from the inner wall of the cylinder.
  • the lubricating medium is able to The plate groove has a good lubrication effect, and can also take away the heat generated by each component, which is beneficial to improving the stability of the pump body component.
  • Figure 1 shows an exploded view of a pump body assembly according to an alternative embodiment of the invention
  • FIG. 2 shows a cross-sectional view of the pump body assembly in FIG. 1;
  • FIG. 3 shows an enlarged view at A in FIG. 2;
  • FIG. 4 shows an enlarged view at B in FIG. 2;
  • FIG. 5 is a schematic diagram showing a positional relationship between a main shaft and a bearing cylinder in FIG. 1;
  • FIG. 6 is a schematic structural diagram of a bearing cylinder in FIG. 1; FIG.
  • FIG. 7 illustrates a cross-sectional view of the main shaft in FIG. 1;
  • FIG. 8 illustrates a top view of the main shaft in FIG. 1;
  • FIG. 9 is a schematic structural diagram of an upper flange in FIG. 1; FIG.
  • FIG. 10 is a cross-sectional view taken along A-A in FIG. 9; FIG.
  • FIG. 11 shows a structural schematic diagram of the lower flange in FIG. 1
  • FIG. 12 shows a sectional view of the lower flange in FIG. 11;
  • FIG. 13 illustrates a cross-sectional view of a pump body assembly according to another alternative embodiment of the present invention.
  • FIG. 14 shows a cross-sectional view of a pump body assembly according to another alternative embodiment of the present invention.
  • orientation words such as “up, down, top, and bottom” are usually used for the directions shown in the drawings, or for the components themselves in the vertical, In terms of vertical or gravity direction; likewise, for the convenience of understanding and description, “inside and outside” means inside and outside relative to the outline of each component itself, but the above orientation words are not used to limit the present invention.
  • the present invention provides a pump body assembly and a compressor.
  • the compressor has a pump body assembly described below.
  • the pump body assembly includes a main shaft 100, and the main shaft 100 has a sliding blade groove 110.
  • the rear end of the sliding blade groove 110 is a back pressure oil chamber 120, and the back pressure oil chamber 120 is at least a part of an oil passage.
  • the oil outlet 121 of the back pressure oil chamber is located on the top of the back pressure oil chamber 120, and the position of the oil inlet 122 of the back pressure oil chamber is lower than the position of the oil outlet 121 of the back pressure oil chamber, so that the lubrication medium passes through.
  • the oil inlet 122 of the back pressure oil chamber enters the back pressure oil chamber 120 and fills the back pressure oil chamber 120, and then flows out from the top of the back pressure oil chamber 120.
  • a lubricating medium can be injected into the back pressure oil chamber 120 to provide back pressure to the sliding plate 150 in the sliding blade groove 110.
  • the position of the oil inlet 122 of the chamber is lower than the position of the oil outlet 121 of the back pressure oil chamber. Therefore, when the lubricating medium flows into the back pressure oil chamber 120, it can effectively ensure that the back pressure oil chamber 120 is always kept full of oil.
  • sufficient back pressure is provided for the sliding plate 150 to ensure that the head of the sliding plate 150 is always close to the inner wall of the bearing cylinder 400, to reduce the leakage problem of the sliding plate 150 head, and to prevent the sliding plate 150 from being easily returned and detached from the inner wall of the cylinder.
  • the head of the sliding plate 150 can be effectively prevented from detaching from the bearing cylinder 400, causing repeated impact between the sliding plate 150 and the bearing cylinder 400 and increasing the noise and vibration of the pump body component, affecting the sliding plate 150 and the pump body component
  • the lubricating medium flowing through the back pressure oil chamber 120 it can have a good lubricating effect on the vane groove 110, and it can also take away the heat generated during the movement of the friction pairs, which is beneficial to Raising pump body components Qualitative.
  • the back pressure at the tail of the sliding plate 150 may not be sufficient to ensure that the sliding plate 150 is always in close contact during the exhaust phase.
  • the sliding plate 150 has the risk of detachment, which can easily cause the sliding plate 150 to impact, affecting the reliability of the sliding plate 150 and the noise and vibration of the compressor. Therefore, ensure that the back pressure oil chamber 120 is full of oil and improve the exhaust section slip.
  • the back pressure of the blade 150 to ensure that the sliding blade 150 does not return is critical to the reliability of the compressor and the noise and vibration.
  • the main shaft 100 also has a central oil hole 130 extending upward from the bottom and a radial oil hole 140 communicating with the central oil hole 130.
  • the central oil hole 130 and the radial oil hole 140 constitute an oil passageway. Part of the lubricating medium flows through the central oil hole 130 and the radial oil hole 140 to the back pressure oil chamber 120.
  • An oil deflector 500 is provided in the central oil hole 130.
  • the oil deflector 500 assembled in the central oil hole 130 rotates to convey the lubricating medium from the bottom of the central oil hole 130 to the upper portion.
  • the lubricating medium in the central oil hole 130 enters the radial oil hole 140 under the action of centrifugal force, and enters the back pressure oil chamber 120 through the radial oil hole 140.
  • central oil hole 130 is a blind hole.
  • the position of the radial oil hole 140 is lower than the position of the oil inlet 122 of the back pressure oil chamber.
  • the pump body assembly further includes a lower flange 200, and the lower flange 200 faces the back pressure oil chamber 120.
  • a lower flange oil passing structure 210 is provided on one side of the surface.
  • the radial oil hole 140 communicates with the oil inlet 122 of the back pressure oil chamber through the lower flange oil passing structure 210.
  • the lower flange oil passing structure 210 is oil. Part of the road passage.
  • the lubricating medium enters the radial oil hole 140 from the central oil hole 130, enters the lower flange oil passing structure 210 from the radial oil hole 140, and finally enters the back pressure oil chamber 120.
  • the position of the radial oil hole 140 is Position lower than the oil inlet 122 of the back pressure oil chamber, so it can better ensure that the lubricating medium entering the back pressure oil chamber 120 gradually fills the back pressure oil chamber 120 from bottom to top, so that the back pressure oil chamber 120 is always maintained
  • the full oil state provides sufficient back pressure for the sliding plate 150 to ensure that the head of the sliding plate 150 is always in close contact with the inner wall of the bearing cylinder 400.
  • the lower flange oil passing structure 210 is a lower flange back pressure oil groove provided on the lower flange 200.
  • the lower flange back pressure oil groove is a stepped groove, and the stepped groove is away from the main shaft 100.
  • the direction groove is deeper. Designing the bottom flange back pressure oil groove as a stepped groove can better ensure the reliability and continuity of the flow of the lubricating medium, which is conducive to providing sufficient back pressure for the sliding plate 150, thereby improving the stability and reliability of the pump body assembly .
  • the projection of the stepped groove on the lower flange 200 is two arc-shaped structures, and the arc-shaped structure away from the main shaft 100 in the two arc-shaped structures is aligned with the back pressure oil cavity 120. Since the arcuate structure far from the main shaft 100 in the two arcuate structures is aligned with the back pressure oil chamber 120, the lubricating medium flows from the arcuate structure away from the main shaft 100 into the back pressure oil chamber 120 during the operation of the pump body assembly.
  • the pump body assembly further includes an upper flange 300 and a bearing cylinder 400, and an upper flange oil-passing structure 310 is provided on a surface of the upper flange 300 facing the back pressure oil chamber 120; the bearing
  • the air cylinder 400 has a rolling body accommodating cavity 410 and a rolling body 420 disposed in the rolling body accommodating cavity 410.
  • the oil outlet 121 of the back pressure oil chamber communicates with the rolling body accommodating cavity 410 through the upper flange oil-passing structure 310.
  • the upper flange oil passing structure 310 and the rolling body accommodation cavity 410 are part of an oil passage.
  • the lubricating medium flows from the oil outlet 121 of the back pressure oil chamber into the upper flange oil passing structure 310 and flows into the rolling body accommodating cavity 410, which can play a good role in the upper flange oil passing structure 310 and the rolling body accommodating cavity 410.
  • the lubricating effect of the pump can also take away the heat generated by various structures, which is conducive to improving the reliability and stability of the pump body components.
  • the upper flange oil passing structure 310 includes an upper flange back pressure oil groove 311 and a radial oil hole 312 opened along a radial direction of the upper flange 300.
  • the upper flange back pressure oil groove 311 and The oil outlet 121 of the back pressure oil cavity communicates with at least a part of the radial oil hole 312 and the upper flange back pressure oil groove 311; the communication hole 313, and the rolling body accommodation cavity 410 communicates with the radial oil hole through the communication hole 313 312 is connected.
  • the lubricating structure enters the upper flange back pressure oil groove 311 from the oil outlet 121 of the back pressure oil chamber, and enters the radial oil hole 312 from the upper flange back pressure oil groove 311, and then enters the rolling element accommodation through the communication hole 313.
  • the cavity 410 in this process, the lubricating medium plays a good role in lubricating the flowing structure, and at the same time, it can take away the heat generated by each structure, which is beneficial to improving the reliability and stability of the pump body component;
  • the position of the oil through hole 312 is located above the back pressure oil chamber 120, so it can be ensured that the lubricating medium in the back pressure oil chamber 120 is full before it can enter the radial oil hole 312.
  • the projection of the upper flange back pressure oil groove 311 on the upper flange 300 is an arc structure.
  • the upper flange back pressure oil groove 311 adopts an arc structure and is aligned with the back pressure oil cavity 120 to ensure that the lubricating medium in the back pressure oil cavity 120 can smoothly flow into the upper flange 300 to increase the lubrication performance of the upper flange 300 and Take away the heat generated by each component to better ensure the reliability and stability of the pump body components.
  • the upper flange oil passing structure 310 includes an oil separation groove 314.
  • the upper flange back pressure oil groove 311 communicates with the inner wall of the upper flange 300 through the oil separation groove 314, and the inner wall of the upper flange 300 is connected to the main shaft 100.
  • the lubricating medium enters the gap between the inner wall of the upper flange 300 and the main shaft 100, and can lubricate the main shaft 100 and the upper flange 300, so as to reduce the friction between the main shaft 100 and the upper flange 300 and reduce this.
  • the mechanical power consumption at the place protects the main shaft 100 and the upper flange 300, and increases the reliability and stability of the pump body assembly.
  • the ratio of the cross-sectional area of the oil separation groove 314 to the radial oil hole 312 is less than or equal to one. In this way, it is possible to ensure the loss of lubricating medium during the flow of the oil passage, along with the length of the oil passage and the diameter of the pipe, and the amount of lubrication medium required by each structure, making the operation of the pump body assembly more reliable. Use better.
  • the ratio of the cross-sectional area of the oil separation groove 314 to the radial oil hole 312 is 3: 7.
  • the ratio of the cross-sectional area of the oil separation groove 314 to the radial oil hole 312 is 3: 7.
  • most of the oil can flow out from the radial oil hole 312, which guarantees sufficient lubrication and heat dissipation of the bearing cylinder 400, and also ensures that the lubrication medium to the main shaft 100 is sufficient, so that the pump body assembly operates most reliably and has the best use effect.
  • the pump body assembly further includes a lower flange 200.
  • An oil outlet groove 220 is provided on a surface of the lower flange 200 facing the back pressure oil chamber 120.
  • the bottom of the rolling body accommodation chamber 410 and The oil outlet groove 220 communicates, and the oil outlet groove 220 extends to the edge of the lower flange 200.
  • the oil outlet groove 220 is a part of the oil passage. In this way, the lubrication medium enters the oil outlet tank 220 from the bottom of the rolling body accommodating cavity 410, and flows back to the oil tank from the oil outlet tank 220 to realize the circulation of the lubrication medium. Through continuous circulation, the various structures are fully lubricated and taken away. The heat generated guarantees the reliability and stability of the pump body components.
  • the final oil outlet of the oil passage is set on the lower flange 200. This is because the lubricating medium circulates in the oil passage and there will be a pressure loss along the process. If the oil outlet is exposed in the compressor cavity, In high pressure gas, the phenomenon of gas channeling easily occurs when there is pressure fluctuation in the compressor cavity, which is not conducive to filling the back pressure oil cavity 120 with the lubricating medium.
  • By setting the oil outlet on the lower flange 200 at a lower position When the oil level in the compressor cavity is low, it can also ensure that the oil outlet is below the liquid level, avoiding the risk of high-pressure gas channeling.
  • the overall oil circuit design ensures that the area of the initial oil inlet is greater than the area of the final oil outlet, enabling multiple inlets. Less, further ensuring that the back pressure oil chamber 120 is full of oil.
  • the difference from the first embodiment is that the structure of the lower flange 200 is different.
  • the pump body assembly further includes a lower flange 200 having an oil drain hole 230 penetrating axially.
  • the bottom of the rolling body accommodation cavity 410 communicates with the top of the oil drain hole 230.
  • the oil drain hole 230 is part of the oil passage.
  • the lubrication medium enters the drain hole 230 from the bottom of the rolling body accommodation cavity 410, and flows back to the oil pool through the drain hole 230 to realize the circulation of the lubrication medium.
  • the structures are fully lubricated, and Take away the heat generated to ensure the reliability and stability of the pump body components.
  • the difference from the first embodiment is that the structure of the lower flange 200 is different.
  • the pump body assembly further includes a lower flange 200, and an oil drain communication groove 240 is provided on a surface of the lower flange 200 facing the back pressure oil chamber 120;
  • the bearing cylinder 400 includes: an axial oil drain channel 430, the bottom of the rolling body accommodating cavity 410 communicates with the bottom of the axial oil discharge channel 430 through an oil drain communication groove 240;
  • the radial oil drain channel 440, and the top of the axial oil drain channel 430 communicates with the radial oil drain channel 440 and
  • the outer peripheral surface of the bearing cylinder 400 communicates, and the axial oil discharge passage 430 and the radial oil discharge passage 440 are part of the oil passage.
  • the lubrication medium enters the oil drain communication groove 240 from the bottom of the rolling body accommodating cavity 410, flows into the axial oil drain channel 430 through the oil drain communication groove 240, and finally flows back to the oil pool through the radial oil drain channel 440 to achieve lubrication.
  • the circulation of the medium, through the continuous circulation process, fully lubricates each structure, and takes away the heat generated to ensure the reliability and stability of the pump body component operation.
  • the oil passage in the bearing cylinder 400 is U-shaped.
  • the back pressure oil chamber at the tail end of the sliding blade groove is filled with lubricating medium, it can provide sufficient back pressure for the sliding blade in the sliding blade groove to ensure that the head of the sliding blade is always close to the inner wall of the bearing cylinder, reducing the sliding blade.
  • the leakage of the head avoids the risk of the sliding blades being easily returned and detached from the inner wall of the cylinder, which is conducive to improving the performance of the compressor;
  • the head of the sliding vane is effectively prevented from detaching from the bearing cylinder, which causes repeated impacts between the sliding vane and the bearing cylinder and increases the noise and vibration of the pump body component, which affects the reliability of the sliding plate and the pump body component;
  • the lubricating medium can have a good lubricating effect on the sliding plate groove, and can also take away the heat generated by each component, which is beneficial to improve the stability of the pump body components;
  • Compressor components are easy to process and assemble, improve compressor noise and vibration, and improve the overall energy efficiency and reliability of the compressor.

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

Abstract

一种泵体组件和压缩机。泵体组件包括：主轴（100），主轴（100）具有滑片槽（110），滑片槽（110）的尾端是背压油腔（120），背压油腔（120）为油路通道的至少一部分，背压油腔的出油口（121）位于背压油腔（120）的顶部，背压油腔的进油口（122）的位置低于背压油腔的出油口（121）的位置，以使润滑介质经背压油腔的进油口（122）进入背压油腔（120）内并充满背压油腔（120）后由背压油腔（120）的顶部流出。

Description

泵体组件和压缩机 技术领域
本发明涉及压缩机技术领域，具体而言，涉及一种泵体组件和压缩机。
背景技术
滑片式压缩机相比于其他类型的压缩机有着零件简单、无偏心结构、力矩平稳振动小等优点，被应用于广泛领域。滑片式压缩机一般具备有多个滑片，其运行原理为：当主轴旋转时，主轴滑片槽内的滑片会一起作复合运动，前后滑片与主轴、气缸构成的容腔随着主轴的旋转而不断的周期性变化，从而实现压缩或膨胀。因此滑片式压缩机能正常运作的先决条件是在整个运行周期内，滑片头部都必须始终贴紧气缸内壁。而滑片式压缩机运行时，其滑片头部始终受到腔内气体力的作用，要使滑片能伸出滑片槽并贴紧气缸内壁，必须保证滑片尾部有大于头部所受气体力的作用力，即需要给滑片足够的背压力。
发明内容
本发明的主要目的在于提供一种泵体组件和压缩机，以解决现有技术中的滑片背压力不足问题。
为了实现上述目的，根据本发明的一个方面，提供了一种泵体组件，包括：主轴，主轴具有滑片槽，滑片槽的尾端是背压油腔，背压油腔为油路通道的至少一部分，背压油腔的出油口位于背压油腔的顶部，且背压油腔的进油口的位置低于背压油腔的出油口的位置，以使润滑介质经背压油腔的进油口进入背压油腔内并充满背压油腔后由背压油腔的顶部流出。
进一步地，主轴还具有由底部向上延伸的中心油孔以及与中心油孔连通的径向油孔，中心油孔、径向油孔构成油路通道的一部分，润滑介质通过中心油孔、径向油孔流向背压油腔。
进一步地，径向油孔的位置低于背压油腔的进油口的位置，泵体组件还包括下法兰，下法兰朝向背压油腔的一侧的表面上设置有下法兰通油结构，径向油孔通过下法兰通油结构与背压油腔的进油口连通，下法兰通油结构为油路通道的一部分。
进一步地，下法兰通油结构为设置在下法兰上的下法兰背压油槽，下法兰背压油槽为阶梯形槽，且阶梯形槽沿远离主轴的方向槽深更深。
进一步地，阶梯形槽在下法兰上的投影为两个弧形结构，且两个弧形结构中远离主轴的弧形结构与背压油腔对正。
进一步地，泵体组件还包括：上法兰，上法兰朝向背压油腔的一侧的表面上设置有上法兰通油结构；轴承气缸，轴承气缸具有滚动体容置腔和设置在滚动体容置腔内的滚动体，背 压油腔的出油口通过上法兰通油结构与滚动体容置腔连通，上法兰通油结构和滚动体容置腔是油路通道的一部分。
进一步地，上法兰通油结构包括：上法兰背压油槽，上法兰背压油槽与背压油腔的出油口连通；沿上法兰的径向开设的径向通油孔，径向通油孔的至少一部分与上法兰背压油槽连通；连通孔，滚动体容置腔通过连通孔与径向通油孔连通。
进一步地，上法兰背压油槽在上法兰上的投影为弧形结构。
进一步地，上法兰通油结构包括分油槽，上法兰背压油槽通过分油槽与上法兰的内壁连通，上法兰的内壁与主轴之间具有间隙，润滑介质通过上法兰背压油槽、分油槽流入间隙处。
进一步地，分油槽与径向通油孔的横截面积之比是3:7。
进一步地，泵体组件还包括下法兰，下法兰朝向背压油腔的一侧的表面上设置有出油槽，滚动体容置腔的底部与出油槽连通，且出油槽延伸至下法兰的边缘处，出油槽是油路通道的一部分。
进一步地，泵体组件还包括下法兰，下法兰具有轴向贯通的排油孔，滚动体容置腔的底部与排油孔的顶部连通，排油孔是油路通道的一部分。
进一步地，泵体组件还包括下法兰，下法兰朝向背压油腔的一侧的表面上设置有排油连通槽；轴承气缸包括：轴向排油通道，滚动体容置腔的底部通过排油连通槽与轴向排油通道的底部连通；径向排油通道，轴向排油通道的顶部通过径向排油通道与轴承气缸的外周面连通，轴向排油通道和径向排油通道是油路通道的一部分。
根据本发明的另一方面，提供了一种压缩机，包括上述的泵体组件。
应用本发明的技术方案，泵体组件包括主轴，主轴具有滑片槽，滑片槽的尾端是背压油腔，背压油腔为油路通道的至少一部分，背压油腔的出油口位于背压油腔的顶部，且背压油腔的进油口的位置低于背压油腔的出油口的位置，以使润滑介质经背压油腔的进油口进入背压油腔内并充满背压油腔后由背压油腔的顶部流出。
由于滑片槽的尾端是背压油腔，因而可以通过往背压油腔内注入润滑介质，以便为滑片槽内的滑片提供背压力，另外，由于背压油腔的进油口的位置低于背压油腔的出油口的位置，因而在润滑介质流入背压油腔内时，能够有效地保证将背压油腔充满，进而为滑片提供足够的背压力，以保证滑片的头部始终贴紧轴承气缸的内壁，减少滑片头部的泄露问题，避免滑片容易被退回、脱离气缸内壁的风险，这样，可以有效地避免滑片的头部脱离轴承气缸，造成滑片与轴承气缸之间的反复撞击并增加了泵体组件的噪音振动，影响滑片和泵体组件的可靠性；另外，润滑介质在流过背压油腔的过程中，能够对滑片槽起到很好的润滑效果，还能充分地带走各部件产生的热量，有利于提高泵体组件的稳定性。
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个可选实施例的泵体组件的爆炸图；
图2示出了图1中泵体组件的剖视图；
图3示出了图2中A处的放大图；
图4示出了图2中B处的放大图；
图5示出了图1中主轴与轴承气缸的位置关系示意图；
图6示出了图1中轴承气缸的结构示意图；
图7示出了图1中主轴的剖视图；
图8示出了图1中主轴的俯视图；
图9示出了图1中上法兰的结构示意图；
图10示出了图9中A-A向剖视图；
图11示出了图1中下法兰的结构示意图
图12示出了图11中下法兰的剖视图；
图13示出了本发明的另一个可选实施例的泵体组件的剖视图；以及
图14示出了本发明的另一个可选实施例的泵体组件的剖视图。
其中，上述附图包括以下附图标记：
100、主轴；110、滑片槽；120、背压油腔；121、背压油腔的出油口；122、背压油腔的进油口；130、中心油孔；140、径向油孔；150、滑片；200、下法兰；210、下法兰通油结构；220、出油槽；230、排油孔；240、排油连通槽；300、上法兰；310、上法兰通油结构；311、上法兰背压油槽；312、径向通油孔；313、连通孔；314、分油槽；320、堵孔焊；400、轴承气缸；410、滚动体容置腔；420、滚动体；430、轴向排油通道；440、径向排油通道；500、导油片。
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。
需要指出的是，除非另有指明，本申请使用的所有技术和科学术语具有与本申请所属技术领域的普通技术人员通常理解的相同含义。
在本发明中，在未作相反说明的情况下，使用的方位词如“上、下、顶、底”通常是针对附图所示的方向而言的，或者是针对部件本身在竖直、垂直或重力方向上而言的；同样地，为便于理解和描述，“内、外”是指相对于各部件本身的轮廓的内、外，但上述方位词并不用于限制本发明。
为了解决现有技术中的滑片背压力不足的问题，本发明提供了一种泵体组件和压缩机。其中，压缩机具有下述的泵体组件。
实施例一
如图1至图12所示，泵体组件包括主轴100，主轴100具有滑片槽110，滑片槽110的尾端是背压油腔120，背压油腔120为油路通道的至少一部分，背压油腔的出油口121位于背压油腔120的顶部，且背压油腔的进油口122的位置低于背压油腔的出油口121的位置，以使润滑介质经背压油腔的进油口122进入背压油腔120内并充满背压油腔120后由背压油腔120的顶部流出。
由于滑片槽110的尾端是背压油腔120，因而可以通过往背压油腔120内注入润滑介质，以便为滑片槽110内的滑片150提供背压力，另外，由于背压油腔的进油口122的位置低于背压油腔的出油口121的位置，因而在润滑介质流入背压油腔120内时，能够有效地保证背压油腔120始终保持满油状态，进而为滑片150提供足够的背压力，以保证滑片150的头部始终贴紧轴承气缸400的内壁，减少滑片150头部的泄露问题，避免滑片150容易被退回、脱离气缸内壁的风险，这样，可以有效地避免滑片150的头部脱离轴承气缸400，造成滑片150与轴承气缸400之间的反复撞击并增加了泵体组件的噪音振动，影响滑片150和泵体组件的可靠性；另外，润滑介质在流过背压油腔120的过程中，能够对滑片槽110起到很好的润滑效果，还能充分地带走各摩擦副运动时产生的热量，有利于提高泵体组件的稳定性。
需要说明的是，由于润滑介质的沿程压降及过压缩的存在，若背压油腔120不满油，排气阶段时，滑片150尾部的背压可能无法满足保证滑片150始终贴紧气缸内壁的要求，滑片150有脱离的风险，容易造成滑片150撞击，影响滑片150可靠性及压缩机整机的噪音振动，因此保证背压油腔120充满油，提高排气段滑片150的背压力，以确保滑片150不退回，对压缩机可靠性和噪音振动至关重要。
如图1至图3所示，主轴100还具有由底部向上延伸的中心油孔130以及与中心油孔130连通的径向油孔140，中心油孔130、径向油孔140构成油路通道的一部分，润滑介质通过中心油孔130、径向油孔140流向背压油腔120。中心油孔130内设置有导油片500，当主轴100旋转时，装配在中心油孔130内的导油片500旋转，以将润滑介质由中心油孔130底部输送到上部，随着主轴100的旋转，中心油孔130内的润滑介质在离心力的作用下进入径向油孔140，并由径向油孔140进入背压油腔120。
需要说明的是，中心油孔130为盲孔。
如图1、图2所示，径向油孔140的位置低于背压油腔的进油口122的位置，泵体组件还包括下法兰200，下法兰200朝向背压油腔120的一侧的表面上设置有下法兰通油结构210，径向油孔140通过下法兰通油结构210与背压油腔的进油口122连通，下法兰通油结构210为油路通道的一部分。这样，润滑介质由中心油孔130进入径向油孔140，并由径向油孔140进入下法兰通油结构210，最后进入背压油腔120，其中，由于径向油孔140的位置低于背压油腔的进油口122的位置，因而可以更好地保证进入背压油腔120内的润滑介质由下往上逐渐充满背压油腔120，实现背压油腔120始终保持满油状态，进而为滑片150提供足够的背压力，以保证滑片150的头部始终贴紧轴承气缸400的内壁。
如图11、图12所示，下法兰通油结构210为设置在下法兰200上的下法兰背压油槽，下法兰背压油槽为阶梯形槽，且阶梯形槽沿远离主轴100的方向槽深更深。将下法兰背压油槽设计为阶梯形槽能够更好地保证润滑介质流动的可靠性与连续性，有利于为滑片150提供足够的背压力，进而提高泵体组件的稳定性与可靠性。
如图11、图12所示，阶梯形槽在下法兰200上的投影为两个弧形结构，且两个弧形结构中远离主轴100的弧形结构与背压油腔120对正。由于两个弧形结构中远离主轴100的弧形结构与背压油腔120对正，因而在泵体组件的运行过程中，润滑介质由远离主轴100的弧形结构流入背压油腔120。
如图9、图10所示，泵体组件还包括上法兰300和轴承气缸400，上法兰300朝向背压油腔120的一侧的表面上设置有上法兰通油结构310；轴承气缸400具有滚动体容置腔410和设置在滚动体容置腔410内的滚动体420，背压油腔的出油口121通过上法兰通油结构310与滚动体容置腔410连通，上法兰通油结构310和滚动体容置腔410是油路通道的一部分。润滑介质由背压油腔的出油口121进入上法兰通油结构310后流入滚动体容置腔410内，能够对上法兰通油结构310以及滚动体容置腔410起到很好的润滑作用，同时能够带走各结构产生的热量，有利于提高泵体组件的可靠性与稳定性。
如图1、图2所示，上法兰通油结构310包括上法兰背压油槽311和沿上法兰300的径向开设的径向通油孔312，上法兰背压油槽311与背压油腔的出油口121连通；径向通油孔312的至少一部分与上法兰背压油槽311连通；连通孔313，滚动体容置腔410通过连通孔313与径向通油孔312连通。这样，润滑结构由背压油腔的出油口121进入上法兰背压油槽311，并由上法兰背压油槽311进入径向通油孔312后，经过连通孔313进入滚动体容置腔410，在这个过程中，润滑介质对流过的结构起到很好的润滑作用，同时能够带走各结构产生的热量，有利于提高泵体组件的可靠性与稳定性；另外，由于径向通油孔312的位置位于背压油腔120的上方，因而能够保证背压油腔120内的润滑介质充满后才能进入径向通油孔312。
需要说明的是，径向通油孔312远离主轴100的一端采用堵孔焊320的方式进行封堵，加工方便、快捷，当然，也可以采用焊接或螺钉等形式进行封堵。
如图9所示，上法兰背压油槽311在上法兰300上的投影为弧形结构。上法兰背压油槽311采用弧形结构是与背压油腔120对正，以保证背压油腔120内的润滑介质能够顺利流入上 法兰300，以增加上法兰300的润滑性能并带走各部件产生的热量，进而更好地保证泵体组件的可靠性与稳定性。
如图1、图2所示，上法兰通油结构310包括分油槽314，上法兰背压油槽311通过分油槽314与上法兰300的内壁连通，上法兰300的内壁与主轴100之间具有间隙，润滑介质通过上法兰背压油槽311、分油槽314流入间隙处。润滑介质进入上法兰300的内壁与主轴100之间的间隙处，能够对主轴100与上法兰300起到润滑作用，以便于减小主轴100与上法兰300之间的摩擦，降低此处机械功耗，对主轴100与上法兰300起到了很好的保护作用，同时增加了泵体组件的可靠性与稳定性。
可选地，分油槽314与径向通油孔312的横截面积之比小于等于1。这样，能够保证润滑介质在油路通道的流动过程中减少沿程损失，并结合油路通道的长度和管径的大小以及各结构对润滑介质的需求量，使得泵体组件的运行更可靠，使用效果更佳。
优选地，分油槽314与径向通油孔312的横截面积之比是3:7。这样，大部分油能从径向通油孔312流出，保证轴承气缸400的充分润滑和散热，又能确保前往主轴100的润滑介质足够，使得泵体组件的运行最可靠，使用效果最佳。
如图1、图2所示，泵体组件还包括下法兰200，下法兰200朝向背压油腔120的一侧的表面上设置有出油槽220，滚动体容置腔410的底部与出油槽220连通，且出油槽220延伸至下法兰200的边缘处，出油槽220是油路通道的一部分。这样，润滑介质由滚动体容置腔410的底部进入出油槽220，并由出油槽220流回油池，实现润滑介质的循环，通过不断地循环过程，对各结构进行充分润滑，并带走产生的热量，保证泵体组件运行的可靠性与稳定性。
在本实施例中，油路通道的最终出油口设置在下法兰200上，这是因为润滑介质在油路通道中流通后会产生沿程压力损失，若出油口暴露在压缩机腔内高压气体中，则压缩机腔内有压力波动时容易产生气体内窜的现象，不利于润滑介质充满背压油腔120，本发明通过将出油口设置在低位的下法兰200上，即使在压缩机腔内油位较低时，也能保证出油口在液面以下，避免高压气内窜的风险,整体油路设计保证最初进油口面积大于最终出油口面积，实现多进少出，进一步确保背压油腔120满油。
实施例二
与实施例一的区别在于，下法兰200的结构不同。
如图13所示，泵体组件还包括下法兰200，下法兰200具有轴向贯通的排油孔230，滚动体容置腔410的底部与排油孔230的顶部连通，排油孔230是油路通道的一部分。这样，润滑介质由滚动体容置腔410的底部进入排油孔230，并由排油孔230流回油池，实现润滑介质的循环，通过不断地循环过程，对各结构进行充分润滑，并带走产生的热量，保证泵体组件运行的可靠性与稳定性。
实施例三
与实施例一的区别在于，下法兰200的结构不同。
如图14所示，泵体组件还包括下法兰200，下法兰200朝向背压油腔120的一侧的表面上设置有排油连通槽240；轴承气缸400包括：轴向排油通道430，滚动体容置腔410的底部通过排油连通槽240与轴向排油通道430的底部连通；径向排油通道440，轴向排油通道430的顶部通过径向排油通道440与轴承气缸400的外周面连通，轴向排油通道430和径向排油通道440是油路通道的一部分。这样，润滑介质由滚动体容置腔410的底部进入排油连通槽240，并由排油连通槽240流入轴向排油通道430，最后由径向排油通道440流回油池，实现润滑介质的循环，通过不断地循环过程，对各结构进行充分润滑，并带走产生的热量，保证泵体组件运行的可靠性与稳定性。
在本实施例中，轴承气缸400内的油路通道呈U形。
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、由于滑片槽尾端的背压油腔内充满润滑介质，因而可以为滑片槽内的滑片提供足够的背压力，保证滑片的头部始终贴紧轴承气缸的内壁，减少滑片头部的泄露问题，避免滑片容易被退回、脱离气缸内壁的风险，有利于提升压缩机性能；
2、有效地避免滑片的头部脱离轴承气缸，造成滑片与轴承气缸之间的反复撞击并增加了泵体组件的噪音振动，影响滑片和泵体组件的可靠性；
3、解决了轴承气缸的润滑和散热问题，提高了轴承气缸可靠性，减小由轴承气缸引起的吸气加热，提升压缩机性能；
4、润滑介质能够对滑片槽起到很好的润滑效果，还能充分地带走各部件产生的热量，有利于提高泵体组件的稳定性；
5、压缩机零部件加工、装配简单，改善压缩机噪音振动，提升压缩机整体能效和可靠性。
显然，上述所描述的实施例仅仅是本发明一部分的实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都应当属于本发明保护的范围。
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 (14)

  1. 一种泵体组件，其特征在于，包括：
    主轴(100)，所述主轴(100)具有滑片槽(110)，所述滑片槽(110)的尾端是背压油腔(120)，所述背压油腔(120)为油路通道的至少一部分，所述背压油腔的出油口(121)位于所述背压油腔(120)的顶部，且所述背压油腔的进油口(122)的位置低于所述背压油腔的出油口(121)的位置，以使润滑介质经所述背压油腔的进油口(122)进入所述背压油腔(120)内并充满所述背压油腔(120)后由所述背压油腔(120)的顶部流出。
  2. 根据权利要求1所述的泵体组件，其特征在于，所述主轴(100)还具有由底部向上延伸的中心油孔(130)以及与所述中心油孔(130)连通的径向油孔(140)，所述中心油孔(130)、所述径向油孔(140)构成所述油路通道的一部分，所述润滑介质通过所述中心油孔(130)、所述径向油孔(140)流向所述背压油腔(120)。
  3. 根据权利要求2所述的泵体组件，其特征在于，所述径向油孔(140)的位置低于所述背压油腔的进油口(122)的位置，所述泵体组件还包括下法兰(200)，所述下法兰(200)朝向所述背压油腔(120)的一侧的表面上设置有下法兰通油结构(210)，所述径向油孔(140)通过所述下法兰通油结构(210)与所述背压油腔的进油口(122)连通，所述下法兰通油结构(210)为所述油路通道的一部分。
  4. 根据权利要求3所述的泵体组件，其特征在于，所述下法兰通油结构(210)为设置在所述下法兰(200)上的下法兰背压油槽，所述下法兰背压油槽为阶梯形槽，且所述阶梯形槽沿远离所述主轴(100)的方向槽深更深。
  5. 根据权利要求4所述的泵体组件，其特征在于，所述阶梯形槽在所述下法兰(200)上的投影为两个弧形结构，且两个所述弧形结构中远离所述主轴(100)的所述弧形结构与所述背压油腔(120)对正。
  6. 根据权利要求1至5中任一项所述的泵体组件，其特征在于，所述泵体组件还包括：
    上法兰(300)，所述上法兰(300)朝向所述背压油腔(120)的一侧的表面上设置有上法兰通油结构(310)；
    轴承气缸(400)，所述轴承气缸(400)具有滚动体容置腔(410)和设置在所述滚动体容置腔(410)内的滚动体(420)，所述背压油腔的出油口(121)通过所述上法兰通油结构(310)与所述滚动体容置腔(410)连通，所述上法兰通油结构(310)和所述滚动体容置腔(410)是所述油路通道的一部分。
  7. 根据权利要求6所述的泵体组件，其特征在于，所述上法兰通油结构(310)包括：
    上法兰背压油槽(311)，所述上法兰背压油槽(311)与所述背压油腔的出油口(121)连通；
    沿所述上法兰(300)的径向开设的径向通油孔(312)，所述径向通油孔(312)的 至少一部分与所述上法兰背压油槽(311)连通；
    连通孔(313)，所述滚动体容置腔(410)通过所述连通孔(313)与所述径向通油孔(312)连通。
  8. 根据权利要求7所述的泵体组件，其特征在于，所述上法兰背压油槽(311)在所述上法兰(300)上的投影为弧形结构。
  9. 根据权利要求7所述的泵体组件，其特征在于，所述上法兰通油结构(310)包括分油槽(314)，所述上法兰背压油槽(311)通过所述分油槽(314)与所述上法兰(300)的内壁连通，所述上法兰(300)的内壁与所述主轴(100)之间具有间隙，所述润滑介质通过所述上法兰背压油槽(311)、所述分油槽(314)流入所述间隙处。
  10. 根据权利要求9所述的泵体组件，其特征在于，所述分油槽(314)与所述径向通油孔(312)的横截面积之比是3:7。
  11. 根据权利要求6所述的泵体组件，其特征在于，所述泵体组件还包括下法兰(200)，所述下法兰(200)朝向所述背压油腔(120)的一侧的表面上设置有出油槽(220)，所述滚动体容置腔(410)的底部与所述出油槽(220)连通，且所述出油槽(220)延伸至所述下法兰(200)的边缘处，所述出油槽(220)是所述油路通道的一部分。
  12. 根据权利要求6所述的泵体组件，其特征在于，所述泵体组件还包括下法兰(200)，所述下法兰(200)具有轴向贯通的排油孔(230)，所述滚动体容置腔(410)的底部与所述排油孔(230)的顶部连通，所述排油孔(230)是所述油路通道的一部分。
  13. 根据权利要求6所述的泵体组件，其特征在于，所述泵体组件还包括下法兰(200)，所述下法兰(200)朝向所述背压油腔(120)的一侧的表面上设置有排油连通槽(240)；所述轴承气缸(400)包括：
    轴向排油通道(430)，所述滚动体容置腔(410)的底部通过所述排油连通槽(240)与所述轴向排油通道(430)的底部连通；
    径向排油通道(440)，所述轴向排油通道(430)的顶部通过所述径向排油通道(440)与所述轴承气缸(400)的外周面连通，所述轴向排油通道(430)和所述径向排油通道(440)是所述油路通道的一部分。
  14. 一种压缩机，其特征在于，包括权利要求1至13中任一项所述的泵体组件。
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CN107524600A (zh) * 2017-09-29 2017-12-29 珠海格力节能环保制冷技术研究中心有限公司 泵体组件及具有其的压缩机
CN207500118U (zh) * 2017-10-30 2018-06-15 珠海格力电器股份有限公司 旋叶式压缩机及其泵体组件
CN108930651A (zh) * 2018-08-31 2018-12-04 珠海格力电器股份有限公司 泵体组件和压缩机

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