WO2020173118A1 - 泵送组件、压缩机及空调设备 - Google Patents

泵送组件、压缩机及空调设备 Download PDF

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Publication number
WO2020173118A1
WO2020173118A1 PCT/CN2019/114735 CN2019114735W WO2020173118A1 WO 2020173118 A1 WO2020173118 A1 WO 2020173118A1 CN 2019114735 W CN2019114735 W CN 2019114735W WO 2020173118 A1 WO2020173118 A1 WO 2020173118A1
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WIPO (PCT)
Prior art keywords
oil
spindle
oil hole
structure body
hole
Prior art date
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PCT/CN2019/114735
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English (en)
French (fr)
Inventor
胡余生
魏会军
徐嘉
邓丽颖
杨国蟒
梁社兵
万鹏凯
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
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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 EP19916656.2A priority Critical patent/EP3933206A4/en
Priority to US17/299,600 priority patent/US11898562B2/en
Publication of WO2020173118A1 publication Critical patent/WO2020173118A1/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
    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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
    • 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
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • the present disclosure relates to the technical field of compressor equipment, and in particular to a pumping assembly, a compressor, and an air-conditioning equipment.
  • the oil path of the rotary vane compressor must ensure the lubrication of the friction pair.
  • the special structure of the rotary vane compressor needs to provide back pressure to the moving blades through the oil path to prevent the blades from leaving the cylinder. Therefore, the oil circuit design and oil distribution of the rotary vane compressor have a particularly important impact on the overall performance of the compressor.
  • the main purpose of the present disclosure is to provide a pumping assembly, a compressor, and an air-conditioning device to solve the problem that the lubricating oil circuit of the pumping assembly cannot meet the lubrication requirements of the pump body in the prior art.
  • a pumping assembly which includes a first structure, a rolling bearing assembly, a second structure, a third structure, and a main shaft.
  • the main shaft passes through the first structure, The rolling bearing assembly, the second structure body and the third structure body, wherein the pumping assembly includes a plurality of lubricating oil passages, and the multiple lubricating oil passages at least include: a first lubricating oil passage, which passes through the second structure, The sliding vane back pressure cavity of the rotor structure of the main shaft, the third structural member, the second structural member, the rolling elements of the rolling element assembly; the second lubricating oil path, the second lubricating oil path passes through the sliding vane back pressure cavity of the rotor structure of the main shaft , The first structural body pressure relief groove of the first structural body; the third lubricating oil circuit, the third lubricating oil circuit passes through the sliding vane back pressure cavity of the rotor structure of the main shaft, the
  • the first lubricating oil circuit includes the spindle center hole of the spindle, the spindle oil hole with the spindle, the second structure back pressure groove of the second structure, the sliding vane back pressure cavity of the rotor structure of the spindle, and the second structure.
  • the second structure of the second structure is the pressure relief groove
  • the second structure of the second structure is the first oil groove
  • the third structure of the third structure is the first oil hole
  • the third structure of the third structure is the second Oil hole, second structure oil hole of second structure, rolling element of rolling bearing assembly, second structure second oil groove of second structure, outer ring oil hole of rolling bearing assembly, first structure of first structure Body first oil hole
  • the lubricating oil in the first lubricating oil circuit returns to the oil pool from the first oil hole of the first structure body.
  • the second lubricating oil circuit includes the spindle center hole of the spindle, the spindle oil hole with the spindle, the second structure back pressure groove of the second structure, the sliding vane back pressure cavity of the rotor structure of the spindle, and the The first structure back pressure groove of a structure body, the first structure body pressure relief groove of the first structure body, the spiral groove of the first structure body, the lubricating oil in the second lubricating oil path from the spiral groove Go back to the oil pool.
  • the third lubricating oil circuit includes the spindle center hole of the spindle, the spindle oil hole of the spindle, the second structure back pressure groove of the second structure, the sliding vane back pressure cavity of the rotor structure of the spindle, and the spindle oil hole of the spindle.
  • the rolling elements of the rolling bearing assembly, the second structure second oil groove of the second structure, the outer ring oil hole of the rolling bearing assembly, the first structure first oil hole of the first structure, and the third lubricating oil path The lubricating oil from the first oil hole of the first structure returns to the oil pool.
  • the first structure is located above the rolling bearing assembly, and the second structure and the third structure are located below the rolling bearing assembly; or, the first structure is located above the rolling bearing assembly The second structure and the third structure are located above the rolling bearing assembly.
  • the first structure is an upper flange
  • the second structure is a lower flange
  • the third structure is a cover plate
  • the relationship between the diameter d0 of the main shaft and the diameter d1 of the main shaft center hole of the main shaft satisfies:
  • the relationship between the diameter d2 of the spindle oil hole of the spindle and the diameter d1 of the spindle center hole of the spindle satisfies: 0.15d1 ⁇ d2 ⁇ 0.6d1.
  • the diameter d1 of the spindle center hole of the main shaft, the diameter d3 of the first oil hole of the third structure of the third structure, and the diameter d4 of the second oil hole of the third structure of the third structure satisfies: 0.1d1 ⁇ d3 ⁇ d4 ⁇ d5 ⁇ 0.3d1.
  • the diameter d2 of the spindle oil hole of the spindle, the diameter d6 of the second oil hole of the first structure of the first structure, and the diameter d7 of the third oil hole of the first structure of the first structure The relationship of satisfies: 0.3d2 ⁇ d6 ⁇ d7 ⁇ d2.
  • the diameter d3 of the first oil hole of the third structure of the third structure, the diameter d7 of the third oil hole of the first structure of the first structure and the first structure of the first structure satisfies:
  • a compressor including the above-mentioned pumping assembly.
  • an air conditioner including the compressor described above.
  • the pumping assembly in the present disclosure includes a first structure, a rolling bearing assembly, a second structure, a third structure, and a main shaft.
  • the main shaft passes through the first structure, the rolling bearing assembly, and the second structure in sequence.
  • the pumping assembly includes a plurality of lubricating oil circuits
  • the plurality of lubricating oil circuits at least include: a first lubricating oil circuit, a second lubricating oil circuit and a third lubricating Passing through the second structure, the sliding vane back pressure cavity of the rotor structure of the main shaft, the third structure, the second structure, and the rolling element of the rolling element assembly;
  • the second lubricating oil path passes through the sliding vane back pressure cavity of the rotor structure of the main shaft ,
  • the third lubricating oil path passes through the sliding vane back pressure cavity of the rotor structure of the main shaft, the first structural member, and the rolling body of the rolling bearing assembly.
  • the rolling bearing assembly is arranged between the first structure and the second structure, and the first structure, the rolling bearing assembly, the second structure and the third structure can be installed separately.
  • the connected lubricating oil circuit can effectively meet the lubrication and heat dissipation requirements of the pump body.
  • this arrangement can also provide stable back pressure to meet the lubrication requirements of each friction pair.
  • Fig. 1 shows a schematic structural diagram of a pumping assembly according to a specific embodiment of the present disclosure
  • Figure 2 shows a top view of the pumping assembly in Figure 1;
  • Figure 3 shows an enlarged view at B in Figure 2;
  • Figure 4 shows a schematic structural diagram of the pumping assembly in Figure 1 when it is in an oil sump
  • Fig. 5 shows an enlarged view at A in Fig. 4;
  • Figure 6 shows a cross-sectional view of the pumping assembly in Figure 1;
  • Figure 7 shows a cross-sectional view of the pumping assembly in Figure 1 from another direction
  • Figure 8 shows a perspective view of the upper flange in the pumping assembly in Figure 1;
  • Figure 9 shows a top view of the upper flange in the pumping assembly of Figure 8.
  • Figure 10 shows a cross-sectional view of the upper flange in the pumping assembly in Figure 8.
  • Figure 11 shows a schematic structural view of the lower flange in the pumping assembly in Figure 1;
  • Figure 12 shows a top view of the lower flange in the pumping assembly in Figure 11;
  • Figure 13 shows the relationship between A6/A3 and COP of the pumping assembly in Figure 1 under two different working conditions.
  • orientation words used such as “up, down, top, bottom” are usually directed to the direction shown in the drawings, or refer to the vertical, In terms of vertical or gravitational direction; similarly, for ease of understanding and description, “inner and outer” refers to the inner and outer relative to the contour of each component itself, but the above-mentioned orientation words are not used to limit the present disclosure.
  • the present disclosure provides a pumping assembly, a compressor, and an air conditioning device.
  • the air conditioning equipment includes a compressor, and the compressor includes the following pumping components.
  • the pumping assembly in the present disclosure includes a first structure 10, a rolling bearing assembly 20, a second structure 30, a third structure 40 and a main shaft 50.
  • the main shaft 50 passes through the first structure 10, the rolling bearing assembly 20, the second structure 30 and the third structure 40 in sequence.
  • the pumping assembly includes multiple lubricating oil circuits, and the multiple lubricating oil circuits at least include: a first lubricating oil circuit, a second lubricating oil circuit, and a third lubricating oil circuit.
  • the first lubricating oil path passes through the second structure 30, the vane back pressure cavity 52 of the rotor structure 51 of the main shaft 50, the third structure 40, the second structure 30, and the rolling elements 21 of the rolling bearing assembly 20.
  • the second lubricating oil path passes through the sliding vane back pressure cavity 52 of the rotor structure 51 of the main shaft 50 and the first structure pressure relief groove 11 of the first structure 10.
  • the third lubricating oil path passes through the sliding vane back pressure cavity 52 of the rotor structure 51 of the main shaft 50, the first structure 10, and the rolling elements 21 of the rolling bearing assembly 20.
  • An oil pump 80 is installed in the lower part of the pumping assembly to be immersed in the oil pool 90 at the bottom of the compressor.
  • the rolling bearing assembly 20 is arranged between the first structure 10 and the second structure 30, and the first structure 10, the rolling bearing assembly 20, and the second structure can be installed separately.
  • the lubricating oil path between 30 and the third structure 40 can effectively meet the lubrication and heat dissipation requirements of the pump body. At the same time, this arrangement can also provide stable back pressure to meet the lubrication requirements of each friction pair.
  • the first structure 10 is located above the rolling bearing assembly 20.
  • the second structure body 30 and the third structure body 40 are located below the rolling bearing assembly 20.
  • the positional relationship between the first structure 10, the second structure 30, and the third structure 40 can also be adjusted.
  • the second structure 30 and the third structure 40 are arranged above the rolling bearing assembly 20, and the first structure A structure 10 is arranged below the rolling bearing assembly 20.
  • Even if the positional relationship between the first structure body 10, the second structure body 30 and the third structure body 40 is adjusted it is necessary to ensure that the first lubricating oil path, the second lubricating oil path, and the third lubricating oil path meet the above-mentioned paths Claim. In this way, it can be ensured that there is sufficient back pressure in the sliding vane back pressure cavity 52, and the rolling elements 21 are effectively lubricated.
  • the first structure 10 has a first structure pressure relief groove 11, a first structure body first oil hole 12, a first structure body back pressure groove 13, a spiral groove 15, and a first structure Body second oil hole 16 and first structure body third oil hole 17.
  • the second structure 30 has a second structure back pressure groove 31, a second structure pressure relief groove 32, a second structure first oil groove 33, a second structure oil hole 34, and The second structure body second oil groove 35.
  • the third structure body 40 has a third structure body first oil hole 41 and a third structure body second oil hole 42.
  • the first lubricating oil path includes the spindle center hole 53 of the spindle 50, the spindle oil hole 55 of the spindle 50, the second structure back pressure groove 31 of the second structure 30, and the rotor structure 51 of the spindle 50.
  • the lubricating oil in the first lubricating oil passage returns to the oil sump 90 from the first oil hole 12 of the first structure.
  • the second lubricating oil is routed between the spindle center hole 53 of the spindle 50, the spindle oil hole 55 of the spindle 50, the second structure back pressure groove 31 of the second structure 30, and the rotor structure 51 of the spindle 50
  • the lubricating oil in the second lubricating oil passage returns to the oil pool 90 from the spiral groove 15 of the first structure 10.
  • the third lubricating oil is routed between the spindle center hole 53 of the spindle 50, the spindle oil hole 55 of the spindle 50, the second structure back pressure groove 31 of the second structure 30, and the rotor structure 51 of the spindle 50
  • the lubricating oil in the third lubricating oil passage returns to the oil sump 90 from the first oil hole 12 of the first structure.
  • the first structure body 10 is an upper flange
  • the second structure body 30 is a lower flange
  • the third structure body 40 is a lower flange cover.
  • the pumping assembly mainly includes an upper flange, a bearing outer ring 23, a bearing inner ring 24, rolling elements 21, a sliding vane 60, a main shaft 50, a lower flange, a lower flange cover and an oil pump 80.
  • the rolling bearing assembly 20 includes a bearing outer ring 23, a bearing inner ring 24 and rolling elements 21.
  • the outer ring oil hole 22 of the rolling bearing assembly 20 is provided on the bearing outer ring, and the rolling elements 21 are provided on the circumferential periphery of the bearing inner ring 24.
  • the main shaft 50 has a rotor structure 51, the rotor structure 51 has a sliding plate groove 54, and the sliding plate 60 is disposed on the sliding plate groove 54 of the rotor structure 51 of the main shaft 50.
  • the three sliding vanes 60 and the bearing inner ring 24 divide the entire crescent cavity enclosed by the bearing inner ring 24 and the main shaft 50 into 4 independent chambers, namely the first chamber 70, the second chamber 71 and the third chamber 72 and the fourth chamber 73:
  • the first chamber 70 When the head of one of the sliding plates 60 is just at 0°, the volume of the first chamber 70 is 0; these chambers are periodically expanded and contracted to achieve the suction of the compressor Gas and exhaust.
  • the sliding vane 60 and the sliding vane groove 54 form a closed space, which we call the sliding vane back pressure cavity 52.
  • the rotation of the main shaft 50 drives the oil pump 80 to rotate.
  • the oil pump 80 is a positive displacement pump. Under the action of the oil pump 80, oil enters the central hole 53 of the main shaft from the oil pool 90; the oil passes through the main shaft oil hole. 55 enters the back pressure groove 31 of the second structure body and fills the back pressure cavity 52 of the sliding plate.
  • the first structure back pressure groove 13 communicates with the second structure back pressure groove 31 through the sliding vane back pressure cavity 52. When the oil fills the sliding vane back pressure cavity 52, the excess oil will further fill the second structure back pressure groove.
  • the second oil groove 35 enters the outer ring oil hole 22 on the bearing outer ring 23, and is discharged from the pump body through the first oil hole 12 of the first structure; the oil discharged from the pressure relief groove 11 of the first structure is screwed through the first structure 10
  • the tank 15 discharges the pump body.
  • the relationship between the diameter d0 of the main shaft 50 and the diameter d1 of the main shaft center hole 53 of the main shaft 50 satisfies: 0.2d0 ⁇ d1 ⁇ 0.5d0.
  • the relationship between the diameter d2 of the spindle oil hole 55 of the spindle 50 and the diameter d1 of the spindle center hole 53 of the spindle 50 satisfies: 0.15d1 ⁇ d2 ⁇ 0.6d1.
  • the diameter d1 of the spindle center hole 53 of the spindle 50, the diameter d3 of the first oil hole 41 of the third structure, the diameter d4 of the second oil hole 42 of the third structure 40 and the third structure The relationship between the diameter d5 of the second structure oil hole 34 of the second structure 30 satisfies: 0.1d1 ⁇ d3 ⁇ d4 ⁇ d5 ⁇ 0.3d1.
  • the diameter d2 of the spindle oil hole 55 of the spindle 50, the diameter d6 of the second oil hole 16 of the first structure of the first structure 10, and the third oil hole of the first structure of the first structure 10 The relationship between the diameter d7 of 17 satisfies: 0.3d2 ⁇ d6 ⁇ d7 ⁇ d2.
  • the diameter d3 of the first oil hole 41 of the third structure body, the diameter d7 of the third oil hole 17 of the first structure body 10 of the first structure body and the first structure body The relationship between the diameter d8 of the oil hole 12 satisfies: 0.125(d3 ⁇ 2+d7 ⁇ 2) ⁇ 0.5 ⁇ d8 ⁇ (d3 ⁇ 2+d7 ⁇ 2) ⁇ 0.5.
  • the above minimum size limitation of d1, d2, d3, d4, d5, d6, d7, d8 can make the influence of the flow resistance of the oil path small and ensure the smooth flow of the flow path; the maximum size limitation is mainly from the reliability of the bearing structure In consideration of performance, the requirements of both can be taken into consideration within the above-mentioned size range.
  • d1, d2, d3, d4, d5, d6, d7, d8 have the same size setting basis.
  • each oil hole in the oil circuit is designed to meet the above requirements, so that the sliding vane back pressure cavity 52 can be in a full oil state, thereby effectively reducing the oil in the sliding vane back pressure cavity 52.
  • the pressure fluctuation can also satisfy the lubrication of each friction pair.
  • the flow channel area corresponding to each oil hole can be obtained as A1, A2, A3, A4, A5, A6, A7, A8, and the total flow area of the spindle center hole 53 of the spindle 50 is A1 ,
  • the total flow area of the spindle oil hole 55 of the spindle 50 is A2
  • the total flow area of the first oil hole 41 of the third structure is A3
  • the total flow area of the second oil hole 42 of the third structure 40 is A4
  • the total flow area of the second structure oil holes 34 of the second structure 30 is A5, the total flow area of the first structure second oil holes 16 of the first structure 10 is A6, and the first structure 10
  • the total flow area of the third oil holes 17 of the first structure is A7, and the total flow area of the first oil holes 12 of the first structure 10 is A8.
  • FIG. 13 it is a graph of the relationship between A6/A3 and COP under two different working conditions (working condition 1: intermediate working condition, that is, 50% rated working condition, working condition 2: rated working condition). ,
  • working condition 1 intermediate working condition, that is, 50% rated working condition
  • working condition 2 rated working condition
  • the COP is the best, that is, a larger cooling capacity can be obtained under the premise of lower power consumption.
  • the shape of the above-mentioned oil hole is not limited to a circular shape, and may be any irregular shape. As long as the equivalent area of the oil hole is satisfied.

Abstract

一种泵送组件、压缩机及空调设备，其中所述泵送组件包括第一结构体（10）、滚动轴承组件（20）、第二结构体（30）、第三结构体（40）和主轴（50），主轴（50）依次穿过第一结构体（10）、滚动轴承组件（20）、第二结构体（30）和第三结构体（40），其中，泵送组件包括多条润滑油路，多条润滑油路至少包括：第一润滑油路，第一润滑油路经过第二结构体（30）、主轴（50）的转子结构（51）的滑片背压腔（52）、第三结构体（40）、第二结构体（30）、滚动轴承组件（20）的滚动体（21）；第二润滑油路，第二润滑油路经过主轴（50）的转子结构（51）的滑片背压腔（52）、第一结构体（10）的第一结构体泄压槽（11）；第三润滑油路，第三润滑油路经过主轴（50）的转子结构（51）的滑片背压腔（52）、第一结构体（10）、滚动轴承组件（20）的滚动体（21）。该泵送组件解决了现有技术中泵送组件的润滑油路无法满足泵体润滑需求的问题。

Description

泵送组件、压缩机及空调设备
相关申请
本公开是以申请号为201910147053.9，申请日为2019年2月27日，发明名称为“泵体组件、压缩机及空调设备”的中国专利申请为基础，并主张其优先权，该中国专利申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及压缩机设备技术领域，具体而言，涉及一种泵送组件、压缩机及空调设备。
背景技术
旋叶式压缩机的油路一方面要保证摩擦副的润滑，另一方面，旋叶式压缩机的特殊结构需要通过油路给运动叶片提供背压以防止叶片脱离气缸。因此旋叶式压缩机的油路设计及油量分配对压缩机的综合性能影响尤为重要。
目前，旋叶式压缩机仍然存在着一些缺陷。由于法兰的限制，轴承滚动体在滚道上运动产生的热量难以散出，而散热不良则会造成压缩机吸气被加热，从而影响压缩机性能；轴承的润滑是单纯靠泵体腔内气体所携带的油泄漏到轴承滚道内的方式实现的，因此轴承滚道内润滑油的量过小，致使轴承润滑不良、发热严重，从而造成轴承失效。
由上述描述可知，现有技术中存在泵送组件的润滑油路无法满足泵体润滑需求的问题。
发明内容
本公开的主要目的在于提供一种泵送组件、压缩机及空调设备，以解决现有技术中泵送组件的润滑油路无法满足泵体润滑需求的问题。
为了实现上述目的，根据本公开的一个方面，提供了一种泵送组件，包括第一结构体、滚动轴承组件、第二结构体、第三结构体和主轴，主轴依次穿过第一结构体、滚动轴承组件、第二结构体和第三结构体，其中，泵送组件包括多条润滑油路，多条润滑油路至少包括：第一润滑油路，第一润滑油路经过第二结构件、主轴的转子结构 的滑片背压腔、第三结构件、第二结构件、滚动体组件的滚动体；第二润滑油路，第二润滑油路经过主轴的转子结构的滑片背压腔、第一结构体的第一结构体泄压槽；第三润滑油路，第三润滑油路经过主轴的转子结构的滑片背压腔、第一结构件、滚动轴承组件的滚动体。
在一些实施例中，第一润滑油路包括主轴的主轴中心孔、与主轴的主轴油孔、第二结构体的第二结构体背压槽、主轴的转子结构的滑片背压腔、第二结构体的第二结构体泄压槽、第二结构体的第二结构体第一油槽、第三结构体的第三结构体第一油孔、第三结构体的第三结构体第二油孔、第二结构体的第二结构体油孔、滚动轴承组件的滚动体、第二结构体的第二结构体第二油槽、滚动轴承组件的外圈油孔、第一结构体的第一结构体第一油孔，所述第一润滑油路内的润滑油从所述第一结构体第一油孔回到油池。
在一些实施例中，第二润滑油路包括主轴的主轴中心孔、与主轴的主轴油孔、第二结构体的第二结构体背压槽、主轴的转子结构的滑片背压腔、第一结构体的第一结构体背压槽、第一结构体的第一结构体泄压槽、第一结构体的螺旋槽，所述第二润滑油路内的润滑油从所述的螺旋槽回到油池。
在一些实施例中，第三润滑油路包括主轴的主轴中心孔、与主轴的主轴油孔、第二结构体的第二结构体背压槽、主轴的转子结构的滑片背压腔、主轴的转子结构的滑片背压腔、第一结构体的第一结构体背压槽、第一结构体的第一结构体第二油孔、第一结构体的第一结构体第三油孔、滚动轴承组件的滚动体、第二结构体的第二结构体第二油槽、滚动轴承组件的外圈油孔、第一结构体的第一结构体第一油孔，所述第三润滑油路内的润滑油从所述第一结构体第一油孔回到油池。
在一些实施例中，第一结构体位于滚动轴承组件的上方，所述第二结构体和所述第三结构体位于所述滚动轴承组件的下方；或者，所述第一结构体位于所述滚动轴承组件的下方，所述第二结构体和第三结构体位于滚动轴承组件的上方。
在一些实施例中，第一结构体是上法兰、第二结构体是下法兰，第三结构体是盖板。
在一些实施例中，主轴的直径d0与主轴的主轴中心孔的直径d1之间的关系满足：
0.2d0≤d1≤0.5d0。
在一些实施例中，主轴的主轴油孔的直径d2与主轴的主轴中心孔的直径d1之间的关系满足：0.15d1≤d2≤0.6d1。
在一些实施例中，主轴的主轴中心孔的直径d1、所述第三结构体的第三结构体第一油孔的直径d3、第三结构体的第三结构体第二油孔的直径d4与第二结构体的第二结构体油孔的直径d5之间的关系满足：0.1d1≤d3≤d4≤d5≤0.3d1。
在一些实施例中，主轴的主轴油孔的直径d2、第一结构体的第一结构体第二油孔的直径d6、第一结构体的第一结构体第三油孔的直径d7之间的关系满足：0.3d2≤d6≤d7≤d2。
在一些实施例中，所述第三结构体的第三结构体第一油孔的直径d3、第一结构体的第一结构体第三油孔的直径d7与第一结构体的第一结构体第一油孔的直径d8之间的关系满足：
0.125(d3^2+d7^2)^0.5≤d8≤(d3^2+d7^2)^0.5。
根据本公开的另一方面，提供了一种压缩机，包括上述的泵送组件。
根据本公开的另一方面，提供了一种空调设备，包括权上述的压缩机。
应用本公开的技术方案，本公开中的泵送组件包括第一结构体、滚动轴承组件、第二结构体、第三结构体和主轴，主轴依次穿过第一结构体、滚动轴承组件、第二结构体和第三结构体，其中，泵送组件包括多条润滑油路，多条润滑油路至少包括：第一润滑油路、第二润滑油路及第三润滑油路；第一润滑油路经过第二结构件、主轴的转子结构的滑片背压腔、第三结构件、第二结构件、滚动体组件的滚动体；第二润滑油路经过主轴的转子结构的滑片背压腔、第一结构体的第一结构体泄压槽；第三润滑油路经过主轴的转子结构的滑片背压腔、第一结构件、滚动轴承组件的滚动体。
在使用上述结构的泵送组件时，通过将滚动轴承组件设置在第一结构体和第二结构体之间，并分别设置能够将第一结构体、滚动轴承组件、第二结构体和第三结构体连通的润滑油路，能够有效地满足泵体的润滑和散热需求。同时，这样设置还能够提供稳定的背压，以满足各摩擦副的润滑的需求。
附图说明
构成本公开的一部分的说明书附图用来提供对本公开的进一步理解，本公开的示意性实施例及其说明用于解释本公开，并不构成对本公开的不当限定。在附图中：
图1示出了根据本公开的一个具体实施例的泵送组件的结构示意图；
图2示出了图1中的泵送组件的俯视图；
图3示出了图2中B处的放大图；
图4示出了图1中的泵送组件处于油池时的结构示意图；
图5示出了图4中的A处的放大图；
图6示出了图1中的泵送组件的剖视图；
图7示出了图1中的泵送组件的另一个方向的剖视图；
图8示出了图1中的泵送组件中的上法兰的透视图；
图9示出了图8中的泵送组件中的上法兰的俯视图；
图10示出了图8中的泵送组件中的上法兰的剖视图；
图11示出了图1中的泵送组件中的下法兰的结构示意图；
图12示出了图11中的泵送组件中的下法兰的俯视图；
图13示出了图1中的泵送组件在两种不同工况下A6/A3与COP的关系曲线图。
具体实施方式
需要说明的是，在不冲突的情况下，本公开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公开。
需要指出的是，除非另有指明，本公开使用的所有技术和科学术语具有与本公开所属技术领域的普通技术人员通常理解的相同含义。
在本公开中，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公开。
为了解决现有技术中泵送组件的润滑油路无法满足泵体润滑需求的问题，本公开提供了一种泵送组件、压缩机及空调设备。
其中，空调设备包括压缩机，压缩机包括下述的泵送组件。
如图1至图12所示，本公开中的泵送组件包括第一结构体10、滚动轴承组件20、第二结构体30、第三结构体40和主轴50。主轴50依次穿过第一结构体10、滚动轴承组件20、第二结构体30和第三结构体40。其中，泵送组件包括多条润滑油路，多条润滑油路至少包括：第一润滑油路、第二润滑油路及第三润滑油路。第一润滑油路经过第二结构体30、主轴50的转子结构51的滑片背压腔52、第三结构体40、第二结构体30、滚动轴承组件20的滚动体21。第二润滑油路经过主轴50的转子结构51的滑片背压腔52、第一结构体10的第一结构体泄压槽11。第三润滑油路经过主轴50 的转子结构51的滑片背压腔52、第一结构体10、滚动轴承组件20的滚动体21。
在泵送组件下部装有油泵80浸在压缩机底部油池90内。在使用上述结构的泵送组件时，通过将滚动轴承组件20设置在第一结构体10和第二结构体30之间，并分别设置能够将第一结构体10、滚动轴承组件20、第二结构体30和第三结构体40连通的润滑油路，能够有效地满足泵体的润滑和散热需求。同时，这样设置还能够提供稳定的背压，以满足各摩擦副的润滑的需求。
在图1所示的具体实施中，第一结构体10位于滚动轴承组件20的上方。第二结构体30和第三结构体40位于滚动轴承组件20的下方。当然，也可以调整第一结构体10、第二结构体30和第三结构体40之间的位置关系，将第二结构体30和第三结构体40设置在滚动轴承组件20的上方，将第一结构体10设置在滚动轴承组件20的下方。即使调整了第一结构体10、第二结构体30和第三结构体40之间的位置关系，也需要保证第一润滑油路、第二润滑油路及第三润滑油路满足上述的路径要求。这样，才能够保证滑片背压腔52内有足够的背压，且滚动体21得到有效的润滑。
如图8至图10所示，第一结构体10具有第一结构体泄压槽11、第一结构体第一油孔12、第一结构体背压槽13、螺旋槽15、第一结构体第二油孔16和第一结构体第三油孔17。如图11和图12所示，第二结构体30具有第二结构体背压槽31、第二结构体泄压槽32、第二结构体第一油槽33、第二结构体油孔34和第二结构体第二油槽35。如图4所示，第三结构体40具有第三结构体第一油孔41和第三结构体第二油孔42。
在该实施例中，第一润滑油路包括主轴50的主轴中心孔53、与主轴50的主轴油孔55、第二结构体30的第二结构体背压槽31、主轴50的转子结构51的滑片背压腔52、第二结构体30的第二结构体泄压槽32、第二结构体30的第二结构体第一油槽33、第三结构体40的第三结构体第一油孔41、第三结构体40的第三结构体第二油孔42、第二结构体30的第二结构体油孔34、滚动轴承组件20的滚动体21、第二结构体30的第二结构体第二油槽35、滚动轴承组件20的外圈油孔22、第一结构体10的第一结构体第一油孔12。第一润滑油路内的润滑油从第一结构体第一油孔12回到油池90。
在该实施例中，第二润滑油路由主轴50的主轴中心孔53、与主轴50的主轴油孔55、第二结构体30的第二结构体背压槽31、主轴50的转子结构51的滑片背压腔52、第一结构体10的第一结构体背压槽13、第一结构体10的第一结构体泄压槽11、第 一结构体10的螺旋槽15。第二润滑油路内的润滑油从第一结构体10的螺旋槽15回到油池90。
在该实施例中，第三润滑油路由主轴50的主轴中心孔53、与主轴50的主轴油孔55、第二结构体30的第二结构体背压槽31、主轴50的转子结构51的滑片背压腔52、第一结构体10的第一结构体背压槽13、第一结构体10的第一结构体第二油孔16、第一结构体10的第一结构体第三油孔17、滚动轴承组件20的滚动体21、第二结构体30的第二结构体第二油槽35、滚动轴承组件20的外圈油孔22、第一结构体10的第一结构体第一油孔12。第三润滑油路内的润滑油从第一结构体第一油孔12回到油池90。
由于在三条润滑油路的流动路径中具有重合的部分，所以在实际的泵送组件的工作过程中，会出现在泵送组件的某些位置处出现三条润滑油路重合的现象。
在图1至图12所示的具体实施例中，第一结构体10是上法兰、第二结构体30是下法兰，第三结构体40是下法兰盖板。如图1所示，泵送组件主要包括上法兰、轴承外圈23、轴承内圈24、滚动体21、滑片60、主轴50、下法兰、下法兰盖板和油泵80。并且，滚动轴承组件20包括轴承外圈23、轴承内圈24和滚动体21，滚动轴承组件20的外圈油孔22设置在轴承外圈上，滚动体21设在轴承内圈24的周向外围。主轴50具有转子结构51，转子结构51具有滑片槽54，滑片60设置在主轴50的转子结构51的滑片槽54上。
如图1至图7所示，压缩机运转时，随着主轴50的旋转，滑片60在离心力和背压的作用下从滑片槽54伸出，并与轴承内圈24内壁面接触。随着压缩机的平稳运行，滑片60在滑片槽54中开始做往复运动。3个滑片60与轴承内圈24把整个由轴承内圈24和主轴50围成的月牙腔分为4个独立的腔室即第一腔室70、第二腔室71、第三腔室72和第四腔室73：当其中一个滑片60头部刚好位于0°时，第一腔室70的容积为0；这几个腔室周期性的扩大、缩小，从而实现压缩机的吸气、排气。压缩机运动过程中，滑片60与滑片槽54形成一个封闭的空间，我们称之为滑片背压腔52，该滑片背压腔52也有三个，并且随着压缩机的运转周期性的放大和缩小。
如图4至图7所示，主轴50旋转带动油泵80旋转，油泵80为一种容积式泵，在油泵80的作用下，油从油池90进入到主轴中心孔53；油通过主轴油孔55进入第二结构体背压槽31，并充满滑片背压腔52。第一结构体背压槽13通过滑片背压腔52与第二结构体背压槽31连通，当油充满滑片背压腔52后，多余的油会进一步填充第 二结构体背压槽31，并通过第一结构体第二油孔16和第一结构体第三油孔17进入轴承内圈24和轴承外圈23之间的空腔74润滑滚动体21；当滑片背压腔52转过一定角度，与第二结构体背压槽31和第一结构体背压槽13脱离后，滑片背压腔52体积继续减小，由滑片背压腔52内排出的油分别通过第二结构体泄压槽32和第一结构体泄压槽11排出；其中经由第二结构体泄压槽32排出的油依次通过第二结构体第一油槽33和第三结构体第一油孔41、第三结构体第二油孔42、第二结构体油孔34进入轴承内圈24和轴承外圈23之间的空腔74，空腔74内的油再经由第二结构体第二油槽35进入轴承外圈23上的外圈油孔22，通过第一结构体第一油孔12排出泵体；由第一结构体泄压槽11排出的油经由第一结构体10螺旋槽15排出泵体。
在一些实施例中，主轴50的直径d0与主轴50的主轴中心孔53的直径d1之间的关系满足：0.2d0≤d1≤0.5d0。
在一些实施例中，主轴50的主轴油孔55的直径d2与主轴50的主轴中心孔53的直径d1之间的关系满足：0.15d1≤d2≤0.6d1。
在一些实施例中，主轴50的主轴中心孔53的直径d1、第三结构体第一油孔41的直径d3、第三结构体40的第三结构体第二油孔42的直径d4与第二结构体30的第二结构体油孔34的直径d5之间的关系满足：0.1d1≤d3≤d4≤d5≤0.3d1。
在一些实施例中，主轴50的主轴油孔55的直径d2、第一结构体10的第一结构体第二油孔16的直径d6、第一结构体10的第一结构体第三油孔17的直径d7之间的关系满足：0.3d2≤d6≤d7≤d2。
在一些实施例中，第三结构体第一油孔41的直径d3、第一结构体10的第一结构体第三油孔17的直径d7与第一结构体10的第一结构体第一油孔12的直径d8之间的关系满足：0.125(d3^2+d7^2)^0.5≤d8≤(d3^2+d7^2)^0.5。
流路中对流动阻力影响主要是两个因素：沿程损失和局部阻力损失，在光滑管的情况下沿程损失可以忽略，主要考虑局部阻力损失的影响，而管径的变化是局部阻力损失的主要影响因素。局部阻力损失hj＝ξ*v^2/(2*g)，流速越小，阻力损失hj越小；局部阻力损失系数ξ越小，阻力损失hj越小，其中，v为管内流体平均速度，g为重力加速度。
以上针对的d1，d2，d3，d4，d5，d6，d7，d8的最小尺寸的限定可以使油路的流动阻力的影响小，保证流路的畅通；最大尺寸的限制主要是从轴承结构可靠性考虑，在以上所述的尺寸范围内能同时兼顾两者的需求。
其中，d1，d2，d3，d4，d5，d6，d7，d8各尺寸设定依据一致。
如图4至图7所示，通过设置油路各油孔的尺寸设计满足上述要求，可以使滑片背压腔52处于满油状态，从而可以有效地减小滑片背压腔52的油压波动，同时还可以满足各摩擦副的润滑。对应的，通过对孔径的换算，可得到各油孔对应的流道面积分别为A1、A2、A3、A4、A5、A6、A7、A8，主轴50的主轴中心孔53的总流通面积为A1，主轴50的主轴油孔55的总流通面积为A2，第三结构体第一油孔41的总流通面积为A3，第三结构体40的第三结构体第二油孔42的总流通面积为A4，第二结构体30的第二结构体油孔34的总流通面积为A5，第一结构体10的第一结构体第二油孔16的总流通面积为A6，第一结构体10的第一结构体第三油孔17的总流通面积为A7，第一结构体10的第一结构体第一油孔12的总流通面积为A8。在一些实施例中，第一结构体10的第一结构体第二油孔16总流通面积A6和第三结构体第一油孔41总流通面积A3的比值满足A6/A3≥2.4，其中以5≤A6/A3≤10时性能最优，其中，性能的评价指标为COP，COP＝制冷量/功耗。
如图13所示，为两种不同工况下(工况1：中间工况，即50％额定工况，工况2：额定工况)A6/A3与COP的关系曲线图，由图可知，在5≤A6/A3≤10时，COP最优，即可以在功耗较小的前提下得到较大的制冷量。
当然，上述油孔的形状不限定于圆形，也可以是任意不规则形状。只要满足油孔的等效面积要求即可。通过优化压缩机油路设计，将油的流动路径设为三个，通过各油孔尺寸控制，首先满足滑片尾部供油的需求，为其提供稳定背压，同时还可以满足各摩擦幅的润滑，提升压缩机的可靠性。
从以上的描述中，可以看出，本公开上述的实施例可以实现如下技术效果至少之一：
1、为各摩擦副提供有效的润滑油路；
2、满足滑片背压需求，同时满足泵体润滑和散热的需求；
3、结构简单，效果明显。
显然，上述所描述的实施例仅仅是本公开一部分的实施例，而不是全部的实施例。基于本公开中的实施例，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，都应当属于本公开保护的范围。
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公开的示例性实施方式。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，本公开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，以便这里描述的本公开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。
以上所述仅为本公开的优选实施例而已，并不用于限制本公开，对于本领域的技术人员来说，本公开可以有各种更改和变化。凡在本公开的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本公开的保护范围之内。

Claims (13)

  1. 一种泵送组件，包括第一结构体(10)、滚动轴承组件(20)、第二结构体(30)、第三结构体(40)和主轴(50)，所述主轴(50)依次穿过所述第一结构体(10)、所述滚动轴承组件(20)、所述第二结构体(30)和所述第三结构体(40)，其中，所述泵送组件包括多条润滑油路，所述多条润滑油路至少包括：
    第一润滑油路，所述第一润滑油路经过所述第二结构体(30)、所述主轴(50)的转子结构(51)的滑片背压腔(52)、所述第三结构体(40)、所述第二结构体(30)、所述滚动轴承组件(20)的滚动体(21)；
    第二润滑油路，所述第二润滑油路经过所述主轴(50)的转子结构(51)的滑片背压腔(52)、所述第一结构体(10)的第一结构体泄压槽(11)；
    第三润滑油路，所述第三润滑油路经过所述主轴(50)的转子结构(51)的滑片背压腔(52)、所述第一结构体(10)、所述滚动轴承组件(20)的滚动体(21)。
  2. 根据权利要求1所述的泵送组件，其中，所述第一润滑油路包括所述主轴(50)的主轴中心孔(53)、与所述主轴(50)的主轴油孔(55)、所述第二结构体(30)的第二结构体背压槽(31)、所述主轴(50)的转子结构(51)的滑片背压腔(52)、所述第二结构体(30)的第二结构体泄压槽(32)、所述第二结构体(30)的第二结构体第一油槽(33)、所述第三结构体(40)的第三结构体第一油孔(41)、所述第三结构体(40)的第三结构体第二油孔(42)、所述第二结构体(30)的第二结构体油孔(34)、所述滚动轴承组件(20)的滚动体(21)、所述第二结构体(30)的第二结构体第二油槽(35)、所述滚动轴承组件(20)的外圈油孔(22)、所述第一结构体(10)的第一结构体第一油孔(12)，所述第一润滑油路内的润滑油从所述第一结构体第一油孔(12)回到油池(90)。
  3. 根据权利要求1所述的泵送组件，其中，所述第二润滑油路包括所述主轴(50)的主轴中心孔(53)、与所述主轴(50)的主轴油孔(55)、所述第二结构体(30)的第二结构体背压槽(31)、所述主轴(50)的转子结构(51)的滑片背压腔(52)、所述第一结构体(10)的第一结构体背压槽(13)、所述第一结构体(10)的第一结构体泄压槽(11)、所述第一结构体(10)的螺旋槽(15)，所述第二润滑油路内的 润滑油从所述螺旋槽(15)回到油池(90)。
  4. 根据权利要求1所述的泵送组件，其中，所述第三润滑油路包括所述主轴(50)的主轴中心孔(53)、与所述主轴(50)的主轴油孔(55)、所述第二结构体(30)的第二结构体背压槽(31)、所述主轴(50)的转子结构(51)的滑片背压腔(52)、所述第一结构体(10)的第一结构体背压槽(13)、所述第一结构体(10)的第一结构体第二油孔(16)、所述第一结构体(10)的第一结构体第三油孔(17)、所述滚动轴承组件(20)的滚动体(21)、所述第二结构体(30)的第二结构体第二油槽(35)、所述滚动轴承组件(20)的外圈油孔(22)、所述第一结构体(10)的第一结构体第一油孔(12)，所述第三润滑油路内的润滑油从所述第一结构体第一油孔(12)回到油池(90)。
  5. 根据权利要求1所述的泵送组件，其中，
    所述第一结构体(10)位于所述滚动轴承组件(20)的上方，所述第二结构体(30)和所述第三结构体(40)位于所述滚动轴承组件(20)的下方；或者
    所述第一结构体(10)位于所述滚动轴承组件(20)的下方，所述第二结构体(30)和所述第三结构体(40)位于所述滚动轴承组件(20)的上方。
  6. 根据权利要求1所述的泵送组件，其中，所述第一结构体(10)是上法兰、所述第二结构体(30)是下法兰，所述第三结构体(40)是盖板。
  7. 根据权利要求1至6中任一项所述的泵送组件，其中，所述主轴(50)的直径d0与所述主轴(50)的主轴中心孔(53)的直径d1之间的关系满足：0.2d0≤d1≤0.5d0。
  8. 根据权利要求1至6中任一项所述的泵送组件，其中，所述主轴(50)的主轴油孔(55)的直径d2与所述主轴(50)的主轴中心孔(53)的直径d1之间的关系满足：0.15d1≤d2≤0.6d1。
  9. 根据权利要求1至6中任一项所述的泵送组件，其中，所述主轴(50)的主轴中心孔(53)的直径d1、所述第三结构体(40)的所述第三结构体第一油孔(41)的 直径d3、所述第三结构体(40)的第三结构体第二油孔(42)的直径d4与所述第二结构体(30)的第二结构体油孔(34)的直径d5之间的关系满足：0.1d1≤d3≤d4≤d5≤0.3d1。
  10. 根据权利要求1至6中任一项所述的泵送组件，其中，所述主轴(50)的主轴油孔(55)的直径d2、所述第一结构体(10)的第一结构体第二油孔(16)的直径d6、所述第一结构体(10)的第一结构体第三油孔(17)的直径d7之间的关系满足：
    0.3d2≤d6≤d7≤d2。
  11. 根据权利要求1至6中任一项所述的泵送组件，其中，所述第三结构体(40)的第三结构体第一油孔(41)的直径d3、所述第一结构体(10)的第一结构体第三油孔(17)的直径d7与所述第一结构体(10)的第一结构体第一油孔(12)的直径d8之间的关系满足：
    0.125(d3^2+d7^2)^0.5≤d8≤(d3^2+d7^2)^0.5。
  12. 一种压缩机，包括权利要求1至11中任一项所述的泵送组件。
  13. 一种空调设备，包括权利要求12所述的压缩机。
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