WO2024239652A1 - 泵体组件、压缩机及空调器 - Google Patents

泵体组件、压缩机及空调器 Download PDF

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Publication number
WO2024239652A1
WO2024239652A1 PCT/CN2023/142614 CN2023142614W WO2024239652A1 WO 2024239652 A1 WO2024239652 A1 WO 2024239652A1 CN 2023142614 W CN2023142614 W CN 2023142614W WO 2024239652 A1 WO2024239652 A1 WO 2024239652A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
groove
cylinder
oil groove
vane
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/CN2023/142614
Other languages
English (en)
French (fr)
Inventor
胡远培
杨欧翔
魏会军
张心爱
刘丹峰
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
Original Assignee
Gree Electric Appliances Inc of Zhuhai
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 Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to EP23938317.7A priority Critical patent/EP4717921A1/en
Publication of WO2024239652A1 publication Critical patent/WO2024239652A1/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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/324—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the inner member and reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C18/3441—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
    • 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
    • F04C18/3442—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 the surfaces of the inner and outer member, forming the inlet and outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • 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
    • F04C2240/10—Stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors
    • 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
    • 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
    • F04C2240/80—Other components

Definitions

  • the present disclosure relates to the technical field of compressors, and in particular to a pump assembly, a compressor and an air conditioner.
  • the energy loss of the compressor can be divided into motor loss, friction loss and indication loss, and friction loss has always accounted for a relatively large proportion of the total loss of the compressor.
  • the friction loss of the compressor is mainly caused by the friction of the friction pairs of the compressor parts during movement. It is mainly caused by the friction loss of the vanes, eccentric bearings, thrust surfaces, main and secondary bearings, rollers, rotor balance blocks and other parts. Research shows that the friction loss of the vanes has always accounted for the largest part of the total friction loss of the compressor. As shown in Figure 1, this friction loss accounts for a larger proportion under high-frequency operation, which can reach about 50% of the total friction loss. Therefore, reducing the friction loss of the vanes is one of the key paths to improve the energy efficiency of the compressor.
  • the present disclosure provides a pump assembly, a compressor and an air conditioner, the main technical problem to be solved is: how to improve the axial balance of the sliding vane and reduce the end surface wear of the sliding vane.
  • the present disclosure mainly provides the following technical solutions:
  • an embodiment of the present disclosure provides a pump body assembly, comprising a cylinder and an oil guide structure, wherein one side of the cylinder is covered with a partition plate, and the other side of the cylinder is covered with a cylinder head, the cylinder has a vane groove for installing a vane, and a first oil groove extending along the axial direction of the cylinder is provided on the side wall of the vane groove, and an oil hole is provided on the partition plate, the oil hole is opposite to a side of the vane away from the cylinder head, and the oil hole is connected to the first oil groove, and the oil guide structure is configured to guide lubricating oil to the oil hole, so that the lubricating oil flows into the first oil groove through the oil hole;
  • a back pressure cavity is formed between the side of the sliding plate facing away from the partition and the cylinder head, and the oil guide structure is also configured to guide the lubricating oil into the back pressure cavity so that the back pressure cavity provides a force for the sliding plate to be relatively close to the partition.
  • the back pressure chamber includes a second oil groove arranged on the cylinder head to receive lubricating oil from the oil guide structure through the second oil groove, and the opening of the second oil groove is opposite to the side of the sliding plate facing away from the partition, and the back pressure chamber provides a force for the sliding plate to be relatively close to the partition through the lubricating oil inside the second oil groove.
  • the second oil groove is communicated with the first oil groove, and the oil guide structure guides the lubricating oil to the second oil groove through the first oil groove.
  • one end of the first oil groove penetrates the vane groove along the axial direction of the cylinder, and an opening of one end of the first oil groove is opposite to an opening of the second oil groove so that the two are connected.
  • the shapes of the opening at one end of the first oil groove and the opening at the second oil groove are adapted to each other so that the opening at one end of the first oil groove is perpendicular to the axial direction of the cylinder.
  • the projection contour on the plane is located on the projection contour of the opening of the second oil groove on the plane perpendicular to the axial direction of the cylinder.
  • the opening shapes of the oil hole and the second oil groove are consistent, and the projection contours of the openings of the two coincide on a plane perpendicular to the axial direction of the cylinder.
  • the opening of the second oil groove exceeds two sides in the thickness direction of the sliding vane.
  • the pump body assembly further includes an oil return structure, and the oil return structure is configured to guide the lubricating oil in the first oil groove and the back pressure chamber to the oil pool.
  • the number of the cylinders is two, and the partition is located between the two cylinders; the number of the cylinder heads is two, and they are arranged one-to-one corresponding to the two cylinders;
  • the number of the back pressure chambers is two, and they are arranged in one-to-one correspondence with the two cylinders.
  • an embodiment of the present disclosure further provides a compressor, which may include any one of the pump body assemblies described above.
  • an embodiment of the present disclosure further provides an air conditioner, which may include any one of the compressors described above.
  • the pump assembly, compressor and air conditioner disclosed in the present invention have at least the following beneficial effects:
  • the back pressure cavity can provide more lubricating oil to the end face of the sliding vane away from the partition, so as to reduce the friction power consumption and improve the energy efficiency of the compressor.
  • the back pressure cavity can provide back pressure to the sliding vane to offset the axial impact of the lubricating oil in the oil hole on the sliding vane, so that the axial force of the sliding vane is more balanced, thereby reducing the end face wear of the sliding vane;
  • FIG1 is a schematic diagram showing the proportion of friction loss in various parts of a compressor
  • FIG2 is a schematic structural diagram of a pump assembly provided by an embodiment of the present disclosure.
  • FIG3 is a schematic diagram of the structure of the pump body assembly in FIG2 when the slide is hidden;
  • FIG4 is an enlarged schematic diagram of point A in FIG3 ;
  • FIG. 5 is a schematic diagram showing the cooperation between the slide on the pump body assembly and the first oil groove and the second oil groove;
  • FIG6 is an enlarged schematic diagram of point B in FIG5;
  • Figure 7 is a schematic diagram of the structure of the upper flange
  • Fig. 8 is a top view of the upper cylinder
  • Fig. 9 is a bottom view of the upper cylinder
  • FIG10 is a schematic diagram of the structure of the partition
  • FIG11 is a cross-sectional view of a partition
  • Fig. 12 is a top view of the lower cylinder
  • Fig. 13 is a bottom view of the lower cylinder
  • FIG. 14 is a schematic diagram of the structure of the lower flange.
  • the pressurized lubricating oil will cause the upper slider to bear an upward axial force and the lower slider to bear a downward axial force, which will cause abnormal wear between the upper end face of the upper slider and the upper flange surface, and between the lower end face of the lower slider and the lower flange surface. This will not only increase the power consumption of the slider end face but also bring new reliability problems. Therefore, it is urgent to solve this situation.
  • a pump body assembly proposed in an embodiment of the present disclosure includes a cylinder 4 and an oil guide structure.
  • a partition plate 5 is covered on one side of the cylinder 4, and a cylinder head 6 is covered on the other side of the cylinder 4.
  • Both the uppermost cylinder 4 and the lowermost cylinder 4 have a cylinder head 6.
  • the cylinder head 6 of the uppermost cylinder 4 can be integrally formed on the upper flange 2
  • the cylinder head 6 of the lowermost cylinder 4 can be integrally formed on the lower flange 9.
  • the aforementioned oil guide structure is configured to guide the lubricating oil to the oil hole 502, so that the lubricating oil flows into the first oil groove 401 through the oil hole 502.
  • the structure of the oil guide structure guiding the lubricating oil to the oil hole 502 is a related technology and will not be repeated here. Among them, since the oil hole 502 is opposite to the side of the slide 16 away from the cylinder head 6, the lubricating oil in the oil hole 502 can flow into the slide groove 406 and lubricate the side of the slide 16 away from the cylinder 4. After the lubricating oil flows into the first oil groove 401, it can also lubricate the side of the slide 16.
  • the number of the first oil grooves 401 is two, and they are respectively arranged on the two opposite side walls of the slide groove 406.
  • the lubricating oil in the two first oil grooves 401 can lubricate the two side surfaces of the slide 16.
  • a back pressure cavity is formed between the side of the sliding vane 16 facing away from the partition 5 and the cylinder head 6 , and the oil guide structure is further configured to guide the lubricating oil into the back pressure cavity so that the back pressure cavity provides a force for the sliding vane 16 to be relatively close to the partition 5 .
  • the back pressure chamber can be set to allow the slide 16 to move away from the partition 5.
  • the end surface of the side provides more lubricating oil, which reduces friction power consumption and improves the energy efficiency of the compressor.
  • the back pressure cavity can provide back pressure to the sliding vane 16 to offset the axial impact of the lubricating oil in the oil hole 502 on the sliding vane 16, so that the axial force of the sliding vane 16 is more balanced, thereby reducing the end surface wear of the sliding vane 16.
  • the back pressure chamber receives lubricating oil through the second oil groove 201 and provides back pressure to the sliding vane 16.
  • the second oil groove 201 is arranged on a side of the cylinder head 6 close to the sliding vane 16, which has the advantage of convenient processing.
  • the aforementioned second oil groove 201 can be connected to the first oil groove 401, and the oil guide structure guides the lubricating oil to the second oil groove 201 through the first oil groove 401.
  • one end of the first oil groove 401 penetrates the vane groove 406 along the axial direction of the cylinder, and the opening of one end of the first oil groove 401 is opposite to the opening of the second oil groove 201, so that the two are connected.
  • the first oil groove 401 can be used as a part of the oil guide structure to guide oil to the second oil groove 201, without opening an additional oil circuit to guide oil to the second oil groove 201, thereby having the advantage of simplifying the structure and making the overall oil guide structure more compact.
  • the shapes of the opening at one end of the first oil groove 401 and the opening of the second oil groove 201 are adapted to each other, so that the projection contour of the opening at one end of the first oil groove 401 on a plane perpendicular to the axial direction of the cylinder is located on the projection contour of the opening of the second oil groove 201 on a plane perpendicular to the axial direction of the cylinder.
  • the projection contour of the opening of the second oil groove 201 on a plane perpendicular to the axial direction of the cylinder is a waist shape
  • the projection contour of the opening at one end of the first oil groove 401 on a plane perpendicular to the axial direction of the cylinder is an arc shape
  • the arc shape coincides with the arc segment on the waist shape.
  • the opening shapes of the oil hole 502 and the second oil groove 201 are consistent, and the openings of the two are perpendicular to the cylinder axis.
  • the projection contours of the openings of the two on the plane perpendicular to the axial direction of the cylinder are both waist-shaped and overlap.
  • Such a design is mainly to enable the lubricating oil in the oil hole 502 and the second oil groove 201 to provide approximately the same axial force to the sliding vane 16, so as to balance the axial force of the sliding vane 16.
  • the opening of the second oil groove 201 exceeds both sides of the thickness direction of the sliding vane 16. Since the opening shapes of the oil hole 502 and the second oil groove 201 are consistent, the opening of the oil hole 502 also exceeds both sides of the thickness direction of the sliding vane 16.
  • Such a design is mainly to enable the oil hole 502 and the second oil groove 201 to provide more sufficient lubricating oil for the upper and lower end surfaces of the sliding vane 16, so as to improve the lubrication effect of the end surface of the sliding vane 16 and further reduce friction power consumption.
  • the aforementioned pump body assembly may also include an oil return structure, which is configured to discharge the lubricating oil in the aforementioned first oil groove 401 and the back pressure chamber to the oil pool to form an oil circuit circulation.
  • the circulating oil circuit can not only ensure the lubrication state of the two side surfaces of the sliding vane 16 under the reciprocating motion of the sliding vane 16, but also ensure the lubrication state of the upper and lower end surfaces of the sliding vane 16, thereby greatly reducing the friction power consumption of the sliding vane 16, and at the same time avoiding the wear problem of the sliding vane 16 caused by the high-frequency oil shortage state of the compressor and the wear problem of the end of the sliding vane 16 caused by the axial force of the sliding vane 16.
  • the aforementioned oil return structure may include an oil guide groove 402 disposed on the side of the vane groove 406 close to the cylinder head 6, and one end of the oil guide groove 402 extends to the intersection of the first oil groove 401 and the second oil groove 201, so that the oil guide groove 402 is connected to both the first oil groove 401 and the second oil groove 201, so that the lubricating oil in both the first oil groove 401 and the second oil groove 201 can flow into the oil guide groove 402.
  • the oil return structure guides the lubricating oil in the first oil groove 401 and the second oil groove 201 to the oil pool through the other end of the oil guide groove 402.
  • the number of the aforementioned cylinders 4 is two, namely, an upper cylinder and a lower cylinder.
  • the partition 5 is located between the two cylinders 4.
  • the number of cylinder heads 6 is two, and they are arranged one-to-one with the two cylinders 4.
  • the two cylinder heads 6 are an upper cylinder head and a lower cylinder head, respectively.
  • the upper cylinder head is integrally formed on the upper flange 2
  • the lower cylinder head is integrally formed on the lower flange 9.
  • Back pressure There are two cavities, which are arranged in one-to-one correspondence with the two cylinders 4. In this example, the two back pressure cavities can provide back pressure for the slides 16 in both the upper cylinder and the lower cylinder to balance the forces on the two slides 16 in the axial direction.
  • An embodiment of the present disclosure further provides an air conditioner, which may include any of the above compressors. Due to the above compressor, the back pressure chamber of the air conditioner can provide back pressure to the sliding vane 16 to offset the axial impact of the lubricating oil in the oil hole 502 on the sliding vane 16, so that the axial force of the sliding vane 16 is more balanced, thereby reducing the end surface wear of the sliding vane 16.
  • the present disclosure is to design a pump body assembly, which can be applied to a compressor, and the compressor can be applied to an air conditioner.
  • the pump body assembly includes a cylinder 4 and a cylinder head 6, and the number of cylinders 4 can be two, respectively, an upper cylinder and a lower cylinder.
  • the number of cylinder heads 6 is two, respectively, an upper cylinder head and a lower cylinder head.
  • the upper cylinder head is integrally formed on the upper flange 2
  • the lower cylinder head is integrally formed on the lower flange 9.
  • the pump body assembly also includes a crankshaft 1, which has an upper eccentric portion and a lower eccentric portion, the upper eccentric portion is located in the upper roller 7, the upper roller 7 is sleeved in the inner circle of the upper cylinder, the upper flange 2 and the upper muffler 3 are installed on the upper part of the upper cylinder, and the upper muffler 3, the upper flange 2 and the upper cylinder are locked by the upper screw 13.
  • the lower eccentric portion is located in the lower roller 8, the lower roller 8 is sleeved in the inner circle of the lower cylinder, and the lower flange 9 and the lower muffler 10 are installed at the lower part of the lower cylinder.
  • the partition plate 5 is installed between the lower cylinder and the upper cylinder, and the lower muffler 10, the lower flange 9, the lower cylinder, the partition plate 5, and the upper cylinder are locked by the lower screw 14.
  • the crankshaft 1 passes through the center holes of the above parts respectively.
  • a crankshaft center oil hole is opened in the center of the crankshaft 1, and an oil guide plate 11 is installed in the crankshaft center oil hole.
  • An oil suction pipe 12 is installed at the lower end of the crankshaft center oil hole.
  • Slides 16 are installed in the slide grooves 406 of both the upper cylinder and the lower cylinder, and pump springs are installed at the tail end of each slide 16.
  • the rolling rotor double-cylinder pump assembly mainly includes a crankshaft 1, an oil suction pipe 12, an oil guide
  • the parts such as the plate 11, the partition plate 5, the oil plug 15, the upper cylinder, the lower cylinder, the sliding plate 16, the upper flange 2, the lower flange 9, etc., are provided with a new lubricating oil path for the above parts to achieve the purpose of lubricating the side and end surface of the sliding plate 16.
  • the upper eccentric oil groove 102 and the lower eccentric oil groove 104 are both connected to the center hole 503 of the partition, so the lubricating oil can be directly pumped into the center hole 503 of the partition, by opening a horizontal hole 501 and a vertical hole at the position of the partition 5 corresponding to the vane groove 406, and the vertical hole is the aforementioned oil hole 502.
  • the inner side of the horizontal hole 501 is connected to the center hole 503 of the partition, and the outer side of the horizontal hole 501 is connected to the oil plug hole 504, and the oil plug 15 is added to the oil plug hole 504 to close it.
  • the lubricating oil in the center hole 503 of the partition can be pumped to the vane groove 406 area of the upper cylinder and the lower cylinder.
  • Vertical oil grooves are opened on both side walls of the vane groove 406 of the upper cylinder and the lower cylinder, and the vertical oil grooves are the aforementioned first oil groove 401.
  • the vertical oil groove is connected with the vertical hole (i.e. the aforementioned oil hole 502) on the partition 5.
  • the vertical hole on the partition 5 is preferably a circular hole.
  • the vertical oil grooves (i.e. the aforementioned first oil groove 401) on the upper cylinder and the lower cylinder are preferably semicircular oil grooves.
  • the closest distance d between the first oil groove 401 on the cylinder 4 and the oblique cut 405 of the cylinder 4 should be ensured to be not less than 1 mm.
  • the first oil groove 401 on the cylinder 4 cannot be connected with the spring transverse hole 404.
  • An oil guide groove 402 is provided on the end surface of each cylinder 4 facing away from the partition 5 from the first oil groove 401 to the spring vertical hole 403, so that the lubricating oil in the oil hole 502 on the partition 5 can flow back to the compressor oil pool through the first oil groove 401 on the upper cylinder, the upper end surface oil guide groove 402 of the upper cylinder and the upper cylinder spring vertical hole 403, and can flow back to the compressor oil pool through the first oil groove 401 on the lower cylinder and the lower end surface oil guide groove 402 of the lower cylinder.
  • an end surface oil groove is provided at the upper flange 2 corresponding to the first oil groove 401 on the upper cylinder, and the end surface oil groove is the aforementioned second oil groove 201.
  • first oil grooves 401 on both sides of the upper cylinder vane groove 406 can be connected through the second oil groove 201 on the upper flange 2, and the lower flange 9 corresponds to the first oil groove 401 of the lower cylinder.
  • An end surface oil groove is also provided, which is the aforementioned second oil groove 201.
  • the first oil grooves 401 on both sides of the lower cylinder vane groove 406 can be connected through the second oil groove 201 on the lower flange 9.
  • the circulating oil circuit can not only ensure the lubrication of the two sides of the vane 16 under the reciprocating motion of the vane 16, but also ensure the lubrication of the upper and lower end surfaces of the vane 16, greatly reducing the friction power consumption of the vane 16, and avoiding the wear problem of the vane 16 caused by the high-frequency oil shortage of the compressor and the wear problem of the end of the vane 16 caused by the axial force of the vane 16.
  • the vertical oil holes on the aforementioned partition 5 i.e. the aforementioned oil holes 502
  • the vertical oil grooves on each cylinder 4 i.e. the aforementioned first oil grooves 401
  • the end face oil grooves on each flange i.e. the aforementioned second oil grooves 201
  • the technical solution disclosed in the present invention can solve the following technical problems: 1. The problem of low energy efficiency of the compressor caused by excessive friction loss of the vane 16; 2. Solving the problem of balancing the axial force of the vane 16 to avoid wear caused by the up and down tilting of the vane 16; 3. Solving the reliability problem of severe wear on the end face of the vane 16 caused by lack of oil in the vane groove 406.
  • the technical solution disclosed in the present invention has the following beneficial effects: 1.
  • the oil supply between the friction pairs of the compressor is more sufficient, the friction power consumption is reduced, and the energy efficiency of the compressor is improved; 2.
  • the axial force of the sliding vane 16 is more balanced, and the end surface lubrication of the sliding vane 16 is more sufficient, which solves the problem of end surface wear of the sliding vane 16; 3.
  • the end surface and side surface of the sliding vane 16 do not need to use the sliding vane 16 coating technology, which reduces the cost of the compressor.

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

Abstract

本申请属于压缩机技术领域。一种泵体组件、压缩机及空调器，泵体组件包括气缸和导油结构，气缸的一侧盖合有隔板，气缸的另一侧盖合有缸盖，气缸具有供滑片安装的滑片槽，滑片槽的侧壁上设有沿气缸轴向延伸的第一油槽，隔板上设有油孔，油孔与滑片背离缸盖的一侧相对，且油孔与第一油槽连通，导油结构被设置为将润滑油导至油孔，使润滑油经油孔流入第一油槽；滑片背离隔板的一侧与缸盖之间形成背压腔，导油结构还被设置为将润滑油导至背压腔内，使背压腔提供滑片相对靠近隔板的力。根据本申请的技术方案，通过设置的背压腔，可以对滑片提供背压，以平衡油孔内的润滑油对滑片的轴向冲击，使滑片轴向受力更平衡，从而可以降低滑片的端面磨损。

Description

泵体组件、压缩机及空调器
本公开要求于2023年05月23日提交中国专利局、申请号为202310587378.5、发明名称为“泵体组件、压缩机及空调器”的中国专利申请的优先权，其全部内容通过引用结合在本公开中。
技术领域
本公开涉及压缩机技术领域，特别是涉及一种泵体组件、压缩机及空调器。
背景技术
在全球绿色低碳环保的大环境下，空调压缩机能效提升一直是行业研究的热点。压缩机的能耗损失可分为电机损失、摩擦损失和指示损失，摩擦损失在压缩机总损失中一直占比较重。压缩机摩擦损失主要由压缩机零部件在运动过程中摩擦副产生摩擦引起的能耗损失，主要由滑片、偏心轴承、止推面、主副轴承、滚子、转子平衡块等零件引起的摩擦损失，经研究表明，其中滑片的摩擦损失一直是压缩机总摩擦损失中占比最大的一部分，如图1所示，该摩擦损失在高频运作下占比更大，可达总摩擦损失的50％左右。因此，通过降低滑片摩擦损失是提升压缩机能效的关键路径之一。
压缩机在运行中，滑片在泵弹簧作用下会跟随滚子在滑片槽内往复运行，滑片侧表面与滑片槽壁、上下端面与上下平面间大面积接触产生大量的摩擦损失，随着压缩机频率提升，尤其到高频运行阶段，压缩机内排油率大幅增加，压缩机内油量减少油位大幅下降，通过滑片槽尾部弹簧孔供油量大幅降低，造成滑片与滑片槽内缺油，滑片摩擦功耗大幅增加，严重情况下会引起滑片与滑片槽及上下端面的干摩擦致使滑片磨损严重，带来压缩机的可靠性问题。针对滑片磨损问题， 业界常采用对滑片进行表面涂层强化进行减缓磨损，但滑片涂层会带来较高的压缩机成本提升，因此，为避免压缩机滑片损耗过大、成本过高，急需设计一种保证滑片部位供油充足方案。
发明内容
有鉴于此，本公开提供一种泵体组件、压缩机及空调器，主要所要解决的技术问题是：如何提高滑片轴向上的平衡，降低滑片的端面磨损。
为达到上述目的，本公开主要提供如下技术方案：
第一方面，本公开的实施例提供一种泵体组件，包括气缸和导油结构，所述气缸的一侧盖合有隔板，气缸的另一侧盖合有缸盖，所述气缸具有供滑片安装的滑片槽，所述滑片槽的侧壁上设有沿气缸轴向延伸的第一油槽，所述隔板上设有油孔，所述油孔与滑片背离缸盖的一侧相对，且油孔与所述第一油槽连通，所述导油结构被设置为将润滑油导至油孔，使润滑油经油孔流入所述第一油槽；
所述滑片背离隔板的一侧与缸盖之间形成背压腔，所述导油结构还被设置为将润滑油导至所述背压腔内，使所述背压腔提供滑片相对靠近所述隔板的力。
在一些实施方式中，所述背压腔包括设置在缸盖上的第二油槽，以通过第二油槽接收导油结构的润滑油，所述第二油槽的开口与所述滑片背离隔板的一侧相对，所述背压腔通过第二油槽内部的润滑油提供滑片相对靠近所述隔板的力。
在一些实施方式中，所述第二油槽与第一油槽连通，所述导油结构通过第一油槽将润滑油导至第二油槽。
在一些实施方式中，所述第一油槽的一端沿气缸轴向贯穿滑片槽，所述第一油槽的一端的开口与第二油槽的开口相对，以使两者连通。
在一些实施方式中，所述第一油槽的一端的开口与第二油槽的开口两者的形状相适配，使第一油槽的一端的开口在垂直于气缸轴向的 平面上的投影轮廓位于第二油槽的开口在垂直于气缸轴向的平面上的投影轮廓上。
在一些实施方式中，所述油孔与第二油槽两者的开口形状一致，且两者的开口在垂直于气缸轴向的平面上的投影轮廓重合。
在一些实施方式中，所述第二油槽的开口超出滑片厚度方向的两侧。
在一些实施方式中，所述的泵体组件还包括回油结构，所述回油结构被设置为将第一油槽和背压腔内的润滑油导出至油池。
在一些实施方式中，当背压腔包括设置在缸盖上的第二油槽，且第二油槽与第一油槽连通时，所述回油结构包括设置在滑片槽靠近缸盖一侧的导油槽，所述导油槽的一端延伸至所述第一油槽与第二油槽两者的交汇处，以使导油槽与第一油槽和第二油槽均连通，所述回油结构通过导油槽的另一端将第一油槽和第二油槽内的润滑油导出至油池。
在一些实施方式中，所述气缸的数量为两个，所述隔板位于两个气缸之间；所述缸盖的数量为两个，且与两个气缸一一对应设置；
所述背压腔的数量为两个，且与两个气缸一一对应设置。
第二方面，本公开的实施例还提供一种压缩机，其可以包括上述任一种所述的泵体组件。
第三方面，本公开的实施例还提供一种空调器，其可以包括上述任一种所述的压缩机。
借由上述技术方案，本公开泵体组件、压缩机及空调器至少具有以下有益效果：
1、在本公开提供的技术方案中，通过设置的背压腔可以为滑片背离隔板一侧的端面提供更多的润滑油，使摩擦功耗减小，提升压缩机能效。另外，通过设置的背压腔，可以对滑片提供背压，以抵消油孔内的润滑油对滑片的轴向冲击，使滑片轴向受力更平衡，从而可以降低滑片的端面磨损；
2、滑片的端面和侧面可不采用滑片涂层技术，降低了成本。
上述说明仅是本公开技术方案的概述，为了能够更清楚了解本公开的技术手段，并可依照说明书的内容予以实施，以下以本公开的较佳实施例并配合附图详细说明如后。
附图说明
为了更清楚地说明本公开实施例或相关技术中的技术方案，下面将对实施例或相关技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本公开的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。
图1是压缩机各部分摩擦损失占比的示意图；
图2是本公开的一实施例提供的一种泵体组件的结构示意图；
图3是图2中的泵体组件隐藏滑片时的结构示意图；
图4是图3中A处的放大示意图；
图5是反映泵体组件上的滑片与第一油槽和第二油槽配合的示意图；
图6是图5中B处的放大示意图；
图7是上法兰的结构示意图；
图8是上气缸的俯视图；
图9是上气缸的仰视图；
图10是隔板的结构示意图；
图11是隔板的剖视图；
图12是下气缸的俯视图；
图13是下气缸的仰视图；
图14是下法兰的结构示意图。
附图标记：1、曲轴；2、上法兰；3、上消音器；4、气缸；5、隔板；6、缸盖；7、上滚子；8、下滚子；9、下法兰；10、下消音器；11、导油片；12、吸油管；13、上螺钉；14、下螺钉；15、油塞；16、滑片；101、上偏心油孔；102、上偏心油槽；103、下偏心油孔；104、 下偏心油槽；201、第二油槽；401、第一油槽；402、导油槽；403、弹簧竖孔；404、弹簧横孔；405、斜切口；406、滑片槽；501、横孔；502、油孔；503、隔板中心孔；504、油塞孔。
具体实施方式
下面将结合本公开实施例中的附图，对本公开实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本公开的一部分实施例，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，都属于本公开保护的范围。
需要说明，若本公开实施例中有涉及方向性指示(诸如上、下、左、右、前、后……)，则该方向性指示仅用于解释在某一特定姿态(如附图所示)下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，若本公开实施例中有涉及“第一”、“第二”等的描述，则该“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本公开要求的保护范围之内。
基于相关技术中常规压缩机滑片在高频供油不足带来的能效低及可靠性问题，我司前期曾针对相关技术进行充分对比分析，提出了一种滚动转子双缸压缩机滑片减磨系统的创新专利提案(申请号：202210648504.9)，通过在隔板上对应滑片槽部位开设相互交叉的横向油孔和竖向油孔对气缸上的滑片槽进行供油，该方案可以大幅增加滑片两侧面的润滑，产生降低摩擦功耗并提升可靠性的有益效果，但是该方案中在隔板上开设的竖向油孔与滑片相对，而竖向油孔内的高 压润滑油会引起上滑片承受一个向上的轴向力、下滑片承受一个向下的轴向力，进而造成上滑片上端面与上法兰面、下滑片下端面与下法兰面产生异常磨损的问题，不仅增加了滑片端面功耗还会带来新的可靠性问题，故急需针对这种情况进行解决。
如图2和图3所示，本公开的一个实施例提出的一种泵体组件，包括气缸4和导油结构。气缸4的一侧盖合有隔板5，气缸4的另一侧盖合有缸盖6。气缸4的数量为两个以上，相邻的两气缸4之间均设有隔板5。最上侧气缸4和最下侧气缸4均具有缸盖6。其中，最上侧气缸4的缸盖6可以一体成型在上法兰2上，最下侧气缸4的缸盖6可以一体成型在下法兰9上。
气缸4具有供滑片16安装的滑片槽406。滑片槽406的侧壁上设有沿气缸轴向延伸的第一油槽401，该第一油槽401可以贯穿气缸轴向的两端。隔板5上设有油孔502，该油孔502可以为竖向油孔。油孔502与滑片16背离缸盖6的一侧相对，且油孔502与第一油槽401连通，在一些实施方式中，油孔502与第一油槽401靠近隔板5一侧的侧口相对，以使油孔502与第一油槽401连通。
前述的导油结构被设置为将润滑油导至油孔502，使润滑油经油孔502流入第一油槽401。导油结构将润滑油导至油孔502内的结构为相关技术，在此不再赘述。其中，由于油孔502与滑片16背离缸盖6的一侧相对，从而油孔502内的润滑油可以流入滑片槽406内，且对滑片16背离气缸4的一侧进行润滑。润滑油流入第一油槽401内后还可以对滑片16的侧面进行润滑。在一个具体的应用示例中，如图8和图9所示，第一油槽401的数量为两个，且分别设置在滑片槽406的相对的两个侧壁上，两个第一油槽401内的润滑油可以对滑片16的两个侧面进行润滑。
其中，滑片16背离隔板5的一侧与缸盖6之间形成背压腔，导油结构还被设置为将润滑油导至背压腔内，使背压腔提供滑片16相对靠近隔板5的力。
在上述示例中，通过设置的背压腔可以为滑片16背离隔板5一 侧的端面提供更多的润滑油，使摩擦功耗减小，提升压缩机能效。另外，通过设置的背压腔，可以对滑片16提供背压，以抵消油孔502内的润滑油对滑片16的轴向冲击，使滑片16轴向受力更平衡，从而可以降低滑片16的端面磨损。
在一个具体的应用示例中，如图4至图6所示，前述的背压腔可以包括设置在缸盖6上的第二油槽201，背压腔通过第二油槽201接收导油结构的润滑油。第二油槽201的开口与滑片16背离隔板5的一侧相对，背压腔通过第二油槽201内部的润滑油提供滑片16相对靠近隔板5的力。
在上述示例中，背压腔通过第二油槽201接收润滑油并对滑片16提供背压力，第二油槽201设置在缸盖6的靠近滑片16的一侧，具有方便加工的优点。
前述的第二油槽201可以与第一油槽401连通，导油结构通过第一油槽401将润滑油导至第二油槽201。在一些实施方式中，第一油槽401的一端沿气缸轴向贯穿滑片槽406，第一油槽401的一端的开口与第二油槽201的开口相对，以使两者连通。
在上述示例中，第一油槽401可以作为导油结构的一部分为第二油槽201导油，不用额外再单独开设油路为第二油槽201导油，从而具有简化结构的优点，使整体的导油结构更加紧凑。
在一个具体的应用示例中，如图7和图8所示，第一油槽401的一端的开口与第二油槽201的开口两者的形状相适配，使第一油槽401的一端的开口在垂直于气缸轴向的平面上的投影轮廓位于第二油槽201的开口在垂直于气缸轴向的平面上的投影轮廓上。比如第二油槽201的开口在垂直于气缸轴向的平面上的投影轮廓为腰形，第一油槽401的一端的开口在垂直于气缸轴向的平面上的投影轮廓为弧形，该弧形与腰形上的弧形段重合。如此设计主要是方便第一油槽401内的润滑油可以顺利流入第二油槽201内，以减小润滑油的流动阻力。
在一个具体的应用示例中，如图7和图10所示，前述油孔502与第二油槽201两者的开口形状一致，且两者的开口在垂直于气缸轴 向的平面上的投影轮廓重合。比如两者的开口在垂直于气缸轴向的平面上的投影轮廓均为腰形，且重合。如此设计，主要是使油孔502和第二油槽201两者内的润滑油能够对滑片16提供大致相当的轴向力，以平衡滑片16轴向上的受力。
在一些实施方式中，如图6所示，前述第二油槽201的开口超出滑片16厚度方向的两侧。由于油孔502与第二油槽201两者的开口形状一致，从而油孔502的开口也超出滑片16厚度方向的两侧，如此设计，主要是使油孔502和第二油槽201两者可以为滑片16的上下两侧端面提供更充足的润滑油，以提高滑片16端面的润滑效果，进一步降低摩擦功耗。
前述的泵体组件还可以包括回油结构，回油结构被设置为将前述第一油槽401和背压腔内的润滑油导出至油池，以形成油路的循环，该循环油路在滑片16往复运动下不仅可以保证滑片16两侧面的润滑状态，还能保证滑片16上下端面的润滑状态，大幅减小滑片16摩擦功耗，同时避免了压缩机在高频缺油状态下出现的滑片16磨损问题以及滑片16承受轴向力带来的滑片16端部磨损问题。
如图4所示，当背压腔包括设置在缸盖6上的第二油槽201，且第二油槽201与第一油槽401连通时，前述的回油结构可以包括设置在滑片槽406靠近缸盖6一侧的导油槽402，导油槽402的一端延伸至第一油槽401与第二油槽201两者的交汇处，以使导油槽402与第一油槽401和第二油槽201均连通，使第一油槽401和第二油槽201两者内的润滑油均可以流入导油槽402内。回油结构通过导油槽402的另一端将第一油槽401和第二油槽201内的润滑油导出至油池。
在上述示例中，通过在滑片槽406的一侧设置延伸至第一油槽401与第二油槽201两者交汇处的导油槽402，具有方便加工的优点。
在一个具体的应用示例中，前述气缸4的数量为两个，分别为上气缸和下气缸。隔板5位于两个气缸4之间。缸盖6的数量为两个，且与两个气缸4一一对应设置。两个缸盖6分别为上缸盖和下缸盖，上缸盖一体成型在上法兰2上，下缸盖一体成型在下法兰9上。背压 腔的数量为两个，且与两个气缸4一一对应设置。在本示例中，通过设置的两个背压腔，可以为上气缸和下气缸两者内的滑片16均提供背压力，以平衡两个滑片16轴向上的受力。
本公开的一个实施例还提出一种压缩机，其可以包括上述任一种泵体组件。压缩机由于上述泵体组件的缘故，背压腔可以对滑片16提供背压，以抵消油孔502内的润滑油对滑片16的轴向冲击，使滑片16轴向受力更平衡，从而可以降低滑片16的端面磨损。
本公开的一个实施例还提出一种空调器，其可以包括上述任一种压缩机。空调器由于上述压缩机的缘故，背压腔可以对滑片16提供背压，以抵消油孔502内的润滑油对滑片16的轴向冲击，使滑片16轴向受力更平衡，从而可以降低滑片16的端面磨损。
下面介绍一下本公开的工作原理和优选实施例。
本公开在于设计一种泵体组件，该泵体组件可以应用在压缩机上，该压缩机可以应用在空调器上。在一个具体的应用示例中，如图2至图14所示，泵体组件包括气缸4和缸盖6，气缸4的数量可以为两个，分别为上气缸和下气缸。缸盖6的数量为两个，分别为上缸盖和下缸盖。上缸盖一体成型在上法兰2上，下缸盖一体成型在下法兰9上。泵体组件还包括曲轴1，曲轴1具有上偏心部和下偏心部，上偏心部位于上滚子7内，上滚子7套设在上气缸内圆中，上法兰2和上消音器3安装在上气缸的上部，并利用上螺钉13对上消音器3、上法兰2和上气缸进行锁合。下偏心部位于下滚子8内，下滚子8套设在下气缸内圆中，下法兰9和下消音器10安装在下气缸的下部。隔板5安装在下气缸和上气缸之间，并利用下螺钉14对下消音器10、下法兰9、下气缸、隔板5、上气缸进行锁合。曲轴1分别从上述各零件的中心孔内穿过，曲轴1内部中心开设有曲轴中心油孔，并在曲轴中心油孔内安装有导油片11，曲轴中心油孔的下端安装有吸油管12，上气缸和下气缸两者的滑片槽406内均安装有滑片16，各滑片16的尾端均安设有泵弹簧。
上述的滚动转子双缸泵体组件主要涉及曲轴1、吸油管12、导油 片11、隔板5、油塞15、上气缸、下气缸、滑片16、上法兰2、下法兰9等零件，通过对上述零件开设新的润滑油路达到对滑片16的侧面和端面均进行润滑的目的。通过在曲轴1底端增加吸油管12和在曲轴中心油孔内设置导油片11，可以保证即使在高频油位很低时依然可以将润滑油泵送至泵体内，润滑油在曲轴中心油孔中分别通过上偏心油孔101和下偏心油孔103流至上偏心油槽102和下偏心油槽104，且上偏心油槽102与上偏心部下端面贯通，下偏心油槽104与下偏心部上端面贯通。上偏心油槽102和下偏心油槽104均与隔板中心孔503连通，故润滑油可以直接泵送至隔板中心孔503内，通过在隔板5对应滑片槽406位置开设横孔501及竖孔，该竖孔即为前述的油孔502。横孔501内侧与隔板中心孔503连通，横孔501外侧与油塞孔504连通，油塞孔504内添加有油塞15封闭。如图4所示，可将隔板中心孔503内的润滑油泵送至上气缸和下气缸的滑片槽406区域。上气缸和下气缸的滑片槽406的两侧壁上均开设有竖向油槽，该竖向油槽即为前述的第一油槽401。该竖向油槽与隔板5上的竖孔(即前述的油孔502)相贯通，隔板5上的竖孔最优为圆孔，上气缸和下气缸上的竖向油槽(即前述的第一油槽401)最优为半圆形油槽。为防止压缩腔气体从各气缸4的竖向油槽泄漏，应保证气缸4上的第一油槽401与气缸4的斜切口405之间的最近距离d不低于1mm。为防止润滑油从弹簧横孔404漏出，气缸4上的第一油槽401与弹簧横孔404不能贯通。
各气缸4背离隔板5的一侧端面自第一油槽401至弹簧竖孔403均开设有导油槽402，这样隔板5上的油孔502内的润滑油即可通过上气缸上的第一油槽401、上气缸上端面导油槽402和上气缸弹簧竖孔403流回压缩机油池，以及通过下气缸上的第一油槽401、下气缸下端面导油槽402流回压缩机油池。此外，上法兰2对应上气缸的上的第一油槽401处开设有端面油槽，该端面油槽即为前述的第二油槽201。这样上气缸滑片槽406两侧的第一油槽401可以通过上法兰2上的第二油槽201进行连通，下法兰9对应下气缸的第一油槽401处 也开设有端面油槽，该端面油槽即为前述的第二油槽201。这样下气缸滑片槽406两侧的第一油槽401可以通过下法兰9上的第二油槽201进行连通。该循环油路在滑片16往复运动下不仅可以保证滑片16两侧面的润滑状态，还能保证滑片16上下端面的润滑状态，大幅减小滑片16摩擦功耗，同时避免了压缩机在高频缺油状态下出现的滑片16磨损问题以及滑片16承受轴向力带来的滑片16端部磨损问题。
前述隔板5上的竖向油孔(即前述的油孔502)、各气缸4上的竖向油槽(即前述的第一油槽401)、各法兰上的端面油槽(即前述的第二油槽201)可为圆形、腰型、椭圆形以及组合形状等，最优为圆形，利于加工。
本公开的技术方案可以解决如下技术问题：1、滑片16摩擦损失过大引起压缩机能效低的问题；2、解决滑片16轴向力的平衡问题，避免滑片16产生上下倾斜带来的磨损；3、解决滑片槽406缺油引起滑片16端面严重磨损的可靠性问题。
本公开的技术方案具有以下有益效果：1、压缩机各摩擦副间供油更充足，摩擦功耗减小，提升压缩机能效；2、滑片16轴向受力更平衡，滑片16的端面润滑更充足，解决了滑片16端面磨损的问题；3、滑片16的端面和侧面可不采用滑片16涂层技术，降低了压缩机成本。
以上所述仅为本公开的优选实施例，并非因此限制本公开的专利范围，凡是在本公开的发明构思下，利用本公开说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本公开的专利保护范围内。

Claims (12)

  1. 一种泵体组件，包括气缸(4)和导油结构，所述气缸(4)的一侧盖合有隔板(5)，气缸(4)的另一侧盖合有缸盖(6)，所述气缸(4)具有供滑片(16)安装的滑片槽(406)，所述滑片槽(406)的侧壁上设有沿气缸(4)轴向延伸的第一油槽(401)，所述隔板(5)上设有油孔(502)，所述油孔(502)与滑片(16)背离缸盖(6)的一侧相对，且油孔(502)与所述第一油槽(401)连通，所述导油结构被设置为将润滑油导至油孔(502)，使润滑油经油孔(502)流入所述第一油槽(401)；
    所述滑片(16)背离隔板(5)的一侧与缸盖(6)之间形成背压腔，所述导油结构还被设置为将润滑油导至所述背压腔内，使所述背压腔提供滑片(16)相对靠近所述隔板(5)的力。
  2. 如权利要求1所述的泵体组件，其中，
    所述背压腔包括设置在缸盖(6)上的第二油槽(201)，以通过第二油槽(201)接收导油结构的润滑油，所述第二油槽(201)的开口与所述滑片(16)背离隔板(5)的一侧相对，所述背压腔通过第二油槽(201)内部的润滑油提供滑片(16)相对靠近所述隔板(5)的力。
  3. 如权利要求2所述的泵体组件，其中，
    所述第二油槽(201)与第一油槽(401)连通，所述导油结构通过第一油槽(401)将润滑油导至第二油槽(201)。
  4. 如权利要求3所述的泵体组件，其中，
    所述第一油槽(401)的一端沿气缸(4)轴向贯穿滑片槽(406)，所述第一油槽(401)的一端的开口与第二油槽(201)的开口相对，以使两者连通。
  5. 如权利要求4所述的泵体组件，其中，
    所述第一油槽(401)的一端的开口与第二油槽(201)的开口两者的形状相适配，使第一油槽(401)的一端的开口在垂直于气缸(4)轴向的平面上的投影轮廓位于第二油槽(201)的开口在垂直于气缸(4)轴向的平面上的投影轮廓上。
  6. 如权利要求2至5中任一项所述的泵体组件，其中，
    所述油孔(502)与第二油槽(201)两者的开口形状一致，且两者的开口在垂直于气缸(4)轴向的平面上的投影轮廓重合。
  7. 如权利要求6所述的泵体组件，其中，
    所述第二油槽(201)的开口超出滑片(16)厚度方向的两侧。
  8. 如权利要求1至5、7中任一项所述的泵体组件，其中，还包括回油结构，所述回油结构被设置为将第一油槽(401)和背压腔内的润滑油导出至油池。
  9. 如权利要求8所述的泵体组件，其中，
    当背压腔包括设置在缸盖(6)上的第二油槽(201)，且第二油槽(201)与第一油槽(401)连通时，所述回油结构包括设置在滑片槽(406)靠近缸盖(6)一侧的导油槽(402)，所述导油槽(402)的一端延伸至所述第一油槽(401)与第二油槽(201)两者的交汇处，以使导油槽(402)与第一油槽(401)和第二油槽(201)均连通，所述回油结构通过导油槽(402)的另一端将第一油槽(401)和第二油槽(201)内的润滑油导出至油池。
  10. 如权利要求1至5、7、9中任一项所述的泵体组件，其中，
    所述气缸(4)的数量为两个，所述隔板(5)位于两个气缸(4)之间；所述缸盖(6)的数量为两个，且与两个气缸(4)一一对应设置；
    所述背压腔的数量为两个，且与两个气缸(4)一一对应设置。
  11. 一种压缩机，包括权利要求1至10中任一项所述的泵体组件。
  12. 一种空调器，包括权利要求11中所述的压缩机。
PCT/CN2023/142614 2023-05-23 2023-12-28 泵体组件、压缩机及空调器 Ceased WO2024239652A1 (zh)

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