WO2020258580A1 - 泵体组件、压缩机和空调器 - Google Patents

泵体组件、压缩机和空调器 Download PDF

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Publication number
WO2020258580A1
WO2020258580A1 PCT/CN2019/109666 CN2019109666W WO2020258580A1 WO 2020258580 A1 WO2020258580 A1 WO 2020258580A1 CN 2019109666 W CN2019109666 W CN 2019109666W WO 2020258580 A1 WO2020258580 A1 WO 2020258580A1
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WIPO (PCT)
Prior art keywords
pump body
crankshaft
body assembly
hole
oil guide
Prior art date
Application number
PCT/CN2019/109666
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English (en)
French (fr)
Inventor
郑礼成
李进
Original Assignee
安徽美芝精密制造有限公司
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Filing date
Publication date
Application filed by 安徽美芝精密制造有限公司 filed Critical 安徽美芝精密制造有限公司
Priority to SG11202112999TA priority Critical patent/SG11202112999TA/en
Priority to JP2021569979A priority patent/JP7105387B2/ja
Priority to EP19934533.1A priority patent/EP3957858A4/en
Publication of WO2020258580A1 publication Critical patent/WO2020258580A1/zh
Priority to US17/535,801 priority patent/US11460028B2/en

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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
    • F04C18/356—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
    • F04C29/023—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
    • 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
    • F04C18/3566—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 more than line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • 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
    • 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
    • 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
    • F04C18/04—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 of internal-axis type
    • 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
    • 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
    • F04C18/322—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 outer 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
    • F04C18/32—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
    • F04C18/356—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
    • 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
    • F04C2/02—Rotary-piston machines or pumps 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
    • 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
    • F04C29/028—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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/603—Centering; Aligning
    • 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
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion

Definitions

  • This application relates to the technical field of compressors, and specifically to a pump body assembly, a compressor and an air conditioner.
  • the lubrication of the crankshaft of the compressor pump body in the related art is generally provided by the spiral oiling blade installed in the inner hole of the lower part of the crankshaft.
  • the lubrication of the main shaft and the auxiliary shaft of the crankshaft is mainly provided by providing oil guide grooves in the inner holes of the main bearing and the auxiliary bearing.
  • the size and position design of the oil guide groove is an important factor that affects the lubrication of the crankshaft. If the design is improper, it will cause insufficient oil supply to the crankshaft main shaft when the compressor is running, resulting in aggravated wear of the crankshaft and main bearing. Problems such as breakage will affect the service life of the compressor.
  • This application aims to solve at least one of the technical problems existing in the prior art or related technologies.
  • the first aspect of this application proposes a pump body assembly.
  • the second aspect of the application proposes a compressor.
  • the third aspect of this application proposes an air conditioner.
  • a pump body assembly including: a crankshaft, the crankshaft includes: a main shaft part and an eccentric part connected to the main shaft part, and a center line of the main shaft part and a center line of the eccentric part
  • the distance between the main bearing is e;
  • the main bearing, the main bearing includes the hub part, the main shaft part penetrates the through hole of the hub part, and the wall of the through hole is provided with a first oil guide groove;
  • the cylinder block is provided with a sliding vane groove
  • the crankshaft penetrates the central hole, the main bearing is located on one side of the cylinder, the radius of the central hole is R, the difference between R and e is r; among them, the center of the central hole in the same projection plane and the sliding
  • the value range of the included angle formed by the first line between the center of the plate groove and the second line between the end point of the first oil guide groove at the end of the hub part away from the eccentric part and the center of the through hole is
  • the pump body assembly includes: a crankshaft, a main bearing and a cylinder block.
  • the crankshaft includes a main shaft part and an eccentric part.
  • the main shaft part and the eccentric part are connected.
  • the cylinder is provided with a central hole and communicates with the central hole
  • the crankshaft passes through the central hole of the cylinder, and the main bearing is set on one side of the cylinder.
  • the end point of the first oil guide groove at the end far away from the eccentric part is connected with the center of the through hole of the hub part to form a second line.
  • the first line between the center of the cylinder center hole and the center of the sliding plate groove is defined as the 0° direction
  • the angle increasing direction is the same as the crankshaft rotation direction
  • the first line is along the crankshaft rotation direction
  • the angle corresponding to the second connecting line is the included angle, and the included angle satisfies the relationship:
  • This application defines the first line between the center of the center hole and the center of the sliding plate groove in the same projection plane along the axis of the center hole and the termination point of the first oil guide groove at the end of the hub part away from the eccentric part
  • the relationship between the angle formed by the second connecting line to the center of the through hole, the crankshaft eccentricity e and the center hole radius R of the cylinder block makes the crankshaft deform under the action of external load and contact with the main bearing, the oil groove supplies oil More fully, the oil film in all parts of the crankshaft main shaft is more uniform, thus effectively improving the abnormal wear of the crankshaft main shaft, avoiding problems such as pump body jamming and crankshaft fracture, and improving the service life of the compressor.
  • the pump body assembly in the above technical solution provided by this application may also have the following additional technical features:
  • the number of cylinders of the pump body assembly is one, and the value range of the included angle is less than or equal to 8 ⁇ /9 and Sum, and greater than or equal to 2 ⁇ /3 and Sum.
  • the value range of the included angle satisfies the formula:
  • the number of cylinders of the pump body assembly is at least two, and the value range of the included angle is less than or equal to 7 ⁇ /9 and Sum, and greater than or equal to 11 ⁇ /18 and Sum.
  • the value range of the included angle satisfies the formula:
  • the crankshaft is deformed under the action of external load and comes into contact with the main bearing, the oil groove can provide more oil.
  • the gas force will have multiple peaks, and the balance weight orientation (corresponding to the direction of centrifugal force) is quite different from that of a single-cylinder compressor.
  • the optimal range is not exactly the same as that of a single cylinder. According to the number of cylinders, the position of the oil groove is different to achieve the best lubrication effect.
  • the angle formed by the first connecting line of the pump body assembly in the same projection plane and the third connecting line between the end point of the other end of the first oil guide groove and the center of the through hole is taken
  • the value range is less than or equal to 2 ⁇ and greater than or equal to 3 ⁇ /2.
  • the end point of the other end of the first oil guide groove and the center of the through hole form a third connection line
  • the angle formed by the first connection line and the third connection line has a greater impact on the reliability of the crankshaft.
  • the pump body assembly further includes: a first annular groove, the first annular groove is arranged on the wall of the through hole, and the first oil guide groove is communicated with the first annular groove.
  • the pump body assembly further includes a first annular groove arranged on the wall of the through hole, the first annular groove is in communication with the first oil guide groove, and the annular groove can be further increased by providing an annular groove on the inner surface of the main bearing hub.
  • the oil supply between the hub of the main bearing and the main shaft of the crankshaft improves the lubrication of the main shaft of the crankshaft.
  • the contact area between the hub of the main bearing and the main shaft of the crankshaft is reduced due to the provision of the first annular groove. Thereby reducing the viscous resistance and friction loss between the two, thereby improving compressor performance.
  • the pump body assembly further includes: an oil passing hole, the oil passing hole is arranged in the first annular groove, and the oil passing hole penetrates the hub portion in the direction.
  • the oil hole diameter penetrates the hub part, which can increase the fluidity between the lubricating oil on the inner surface of the hub and the external lubricating oil, and reduce the lubricating oil in the hub to a certain extent. Temperature, thereby further improving the lubrication reliability of the crankshaft main shaft.
  • the radial depth of the first annular groove of the pump body assembly is less than or equal to 0.5 mm.
  • the radial depth of the first annular groove is limited to not greater than 0.5 mm, which ensures that the first annular groove has a small effect on the rigidity of the entire pump body assembly.
  • the pump body assembly further includes: a second annular groove, the second annular groove is arranged on the main shaft portion and is located in the area where the main shaft portion and the hub portion cooperate.
  • the radial depth of the second annular groove of the pump body assembly is less than or equal to 0.5 mm.
  • the radial depth of the second annular groove is limited to no more than 0.5 mm, which ensures the overall rigidity of the crankshaft, thereby ensuring that the second annular groove has a small effect on the rigidity of the entire pump body assembly.
  • crankshaft of the pump body assembly further includes a secondary shaft portion, and the eccentric portion is located between the main shaft portion and the secondary shaft portion;
  • the pump body assembly further includes a secondary bearing, the primary bearing is sleeved on the primary shaft, and the secondary bearing It is sleeved on the secondary shaft part;
  • the pump body assembly further includes: a second oil guide groove which is arranged in the through hole of the secondary bearing.
  • the crankshaft also includes a secondary shaft part connected to the eccentric part, the bearing includes a main bearing and a secondary bearing, the main bearing and the secondary bearing are located on both sides of the cylinder block, the main bearing is matched with the main shaft, and the secondary bearing is The auxiliary shaft part is matched, the main bearing is provided with a first oil guiding groove, and the auxiliary bearing through hole is provided with a second oil guiding groove.
  • the pump body assembly further includes: the first connecting line and the second oil guide groove between the center of the center hole and the center of the sliding plate groove in the same projection plane are at one end of the hub part near the eccentric part
  • the value range of the included angle formed by the fourth connecting line from the end point to the center of the through hole is less than or equal to 2 ⁇ and greater than or equal to 3 ⁇ /2.
  • the second oil guide groove forms a fourth line from the end point of the end near the eccentric part of the hub to the center of the through hole, when the first line
  • the range of the included angle formed by the fourth connecting line is less than or equal to 2 ⁇ and greater than or equal to 3 ⁇ /2, when the crankshaft deforms under the action of external load and contacts the auxiliary bearing, the oil groove supplies more oil and the crankshaft is overall reliable Better.
  • the first oil guide groove and the second oil guide groove of the pump body assembly are both spiral oil guide grooves.
  • the first oil guide groove and the second oil guide groove are arranged as spiral oil guide grooves, which facilitates the flow of lubricating oil during the operation of the compressor, so that the inner wall surfaces of the main bearing and the auxiliary bearing are in the spiral oil guide groove.
  • the lubricating oil is supplied to the crankshaft main shaft and counter shaft, so as to have the effect of lubricating the crankshaft main shaft and counter shaft.
  • the spiral direction of the first oil guide groove and the second oil guide groove of the pump body assembly is the same as the rotation direction of the crankshaft.
  • the spiral direction of the first oil guide groove and the spiral direction of the second oil guide groove are the same as the rotation direction of the crankshaft, so that the lubricating oil can better enter the first oil guide groove and the second oil guide groove under the action of centrifugal force.
  • the spiral direction of the first oil guide groove and the spiral direction of the second oil guide groove are the same to ensure that the lubricating oil is introduced into each position where the crankshaft contacts the hub.
  • the width of the first oil guide groove of the pump body assembly is less than or equal to 5mm and greater than or equal to 1.5mm; the depth of the first oil guide groove is less than or equal to 3mm and greater than Equal to 0.3mm.
  • a compressor including the pump body assembly of any of the above technical solutions. Therefore, it has all the beneficial effects of the pump body assembly, which will not be repeated here.
  • an air conditioner including the pump body assembly or compressor of any of the above technical solutions. Therefore, it has all the beneficial effects of the pump body assembly or compressor, which will not be repeated here.
  • Fig. 1 shows a schematic diagram of a pump body assembly structure in the prior art.
  • Figure 2 shows a schematic diagram of a cylinder structure according to an embodiment of the present application
  • Fig. 3 shows a schematic diagram of the size and angle of the pump body assembly in operation according to an embodiment of the present application
  • FIG. 4 shows a schematic diagram of the end angle of the first oil guide groove of the main bearing of the pump body assembly away from the cylinder side according to an embodiment of the present application
  • FIG. 5 shows a schematic diagram of the end angle of the first oil guide groove of the main bearing of the pump body assembly close to the cylinder side in another embodiment of the present application
  • Fig. 6 shows a schematic diagram of the size structure of the first oil guide groove of the pump body assembly according to an embodiment of the present application
  • Fig. 7 shows a schematic diagram of the bearing structure according to an embodiment of the present application.
  • Fig. 8 shows a schematic diagram of the crankshaft structure according to an embodiment of the present application.
  • FIG. 9 shows a schematic diagram of a bearing structure according to another embodiment of the present application.
  • Fig. 10 shows a structural schematic diagram of a cylinder block of a swing compressor according to an embodiment of the present application
  • FIG. 11 shows a schematic diagram of the hinged structure of a piston sliding piece according to an embodiment of the present application
  • Figure 12 shows the relationship between the included angle of the single-cylinder compressor and the amount of crankshaft wear in an embodiment of the present application
  • Fig. 13 shows the relationship between the included angle of the multi-cylinder compressor and the amount of crankshaft wear in an embodiment of the present application.
  • 1 pump body assembly 10 crankshaft, 102 main shaft part, 104 eccentric part, 106 counter shaft part, 12 main bearing, 120 first oil guide groove, 122 hub part, 124 flange part, 126 first connection, 128 second connection Line, 130 through hole, 142 cylinder, 144 sliding vane groove, 146 center hole, 150 crankshaft rotation direction, 152 third connection, 154 first annular groove, 156 oil hole, 158 piston, 160 sliding vane, 162th Two ring groove.
  • a pump body assembly 1 including: a crankshaft 10, the crankshaft 10 includes: a main shaft portion 102 and an eccentric portion 104 connected to the main shaft portion 102, a center line of the main shaft portion 102 and the eccentric portion 104
  • the pump body assembly 1 includes a crankshaft 10, a main bearing 12, and a cylinder block 142.
  • the crankshaft 10 includes a main shaft portion 102 and an eccentric portion 104, and the main shaft portion 102 and the eccentric portion 104 are connected.
  • the main bearing 12 includes a hub portion 122 and a flange portion 124.
  • the hub portion 122 is provided with a through hole 130, and the hole wall of the through hole 130 A first oil guide groove 120 is provided, the main shaft portion 102 passes through the through hole 130; the cylinder 142 is provided with a central hole 146 and a sliding plate groove 144 communicating with the central hole 146, and the crankshaft 10 passes through the central hole 146 of the cylinder 142 ,
  • the center of the central hole 146 is connected to the center of the sliding vane groove 144 to form a first connecting line 126.
  • the first oil guide groove 120 is located far away from the eccentric portion 104.
  • the end point of one end is connected to the center of the through hole 130 of the hub portion 122 to form a second connection line 128, the angle increasing direction is the same as the crankshaft rotation direction 150, the first connection line 126 rotates along the rotation direction of the crankshaft 10 to the second connection line 128
  • the corresponding angle is the included angle, and the included angle satisfies the relationship:
  • the first connecting line 126 and the first oil guide groove 120 between the center of the center hole 146 and the center of the sliding plate groove 144 defined in the same projection plane along the axis direction of the center hole are located at the hub portion 122 away from the eccentric portion.
  • the angle formed by the second connecting line 128 between the end point of 104 and the center of the through hole 130, the eccentricity e of the crankshaft 10 and the radius R of the central hole 146 of the cylinder block 142 make the crankshaft 10 under external load
  • the oil groove supplies more oil
  • the oil film on the main shaft portion 102 of the crankshaft 10 is more uniform, thereby effectively improving the abnormal wear of the main shaft portion 102 of the crankshaft 10 and avoiding the jam of the pump body and the crankshaft fracture. Problem, improve the service life of the compressor.
  • crankshaft lubrication principle and wear mechanism of the existing compressor with reference to Figure 1:
  • the compressor pump body assembly includes: a crankshaft 10', a bearing and a cylinder 142'.
  • the crankshaft 10' includes a main shaft portion 102', an eccentric portion 104', and a counter shaft portion 106';
  • the bearing includes a main bearing and an auxiliary bearing, the main bearing includes a main bearing profile 122' and a main bearing flange 124', and the main shaft portion 102 'Set at the main bearing profile 122',
  • the secondary bearing includes a secondary bearing hub 132' and a secondary bearing flange 134', the secondary shaft portion 106' is set at the secondary bearing hub 132', and the crankshaft 10' is generally lubricated at 10'
  • the spiral oiling blade 112' installed in the inner hole of the countershaft portion 106' supplies oil.
  • the oiling blade 112' supplies the lubricating oil at the bottom of the compressor oil sump upwards through the crankshaft 10'
  • the oil holes 110' of the main shaft part 102' and the counter shaft part 106' are transmitted to the main bearing inner hole and the auxiliary bearing inner hole, and then the lubricating oil is supplied to the crankshaft main shaft under the action of the spiral oil guide groove on the inner wall surface of the main and auxiliary bearings 102' and the countershaft portion 106', thereby achieving the effect of lubricating the main shaft portion 102' and the countershaft portion 106' of the crankshaft 10'.
  • crankshaft 10' When the compressor is running, the crankshaft 10' is subjected to gas force, radial magnetic pulling force and centrifugal force of the balance weight. The force causes the crankshaft 10' to deform and tilt and contact the bearing to generate contact stress. If the contact stress is too large, or the position of the bearing oil guide groove is set unreasonably, it will cause abnormal wear of the crankshaft and the bearing due to insufficient oil supply.
  • this application Based on the above crankshaft lubrication principle and wear mechanism, combined with the force of the crankshaft, this application conducts in-depth analysis and research on the relationship between the end point of the oil guide groove of the main bearing and the crankshaft eccentricity, the radius of the cylinder block 142, etc., and proposes a
  • the new main bearing 12 has a spiral oil guide groove design structure, which is simple to implement and has significant effects. It should be noted that the structure of the present application is applicable to different refrigerant and lubricating oil compressors.
  • the number of cylinders 142 of the pump body assembly 1 is one, and the value range of the included angle is less than or equal to 8 ⁇ /9 and Sum, and greater than or equal to 2 ⁇ /3 and Sum.
  • the value range of the included angle satisfies the formula:
  • the number of cylinders 142 of the pump body assembly 1 is at least two, and the value range of the included angle is less than or equal to 7 ⁇ /9 and Sum, and greater than or equal to 11 ⁇ /18 and Sum.
  • the value range of the included angle satisfies the formula:
  • the crankshaft 10 is deformed under the action of an external load and comes into contact with the main bearing 12, the oil groove is more fully supplied with oil.
  • the gas force will have multiple peaks, and the balance weight orientation (corresponding to the direction of centrifugal force) is quite different from that of a single-cylinder compressor.
  • the optimal range is not exactly the same as that of a single cylinder. According to the number of cylinders, the position of the oil groove is different to achieve the best lubrication effect.
  • the end point of the other end of the first oil guide groove 120 to the center of the through hole 130 constitutes a third connection line 152, and the angle formed by the first connection line 126 and the third connection line 152 makes the crankshaft 10 reliable.
  • the impact of the performance is greater.
  • the crankshaft 10 will deform under the action of external load and will When the bearing 12 is in contact, the oil groove is more fully supplied with oil, and the reliability of the main shaft portion 102 of the crankshaft 10 is better.
  • the pump body assembly 1 further includes: a first annular groove 154, the first annular groove 154 is provided on the wall of the through hole 130, the first oil guide groove 120 and the second An annular groove 154 communicates with each other.
  • the pump body assembly 1 further includes a first annular groove 154 provided on the wall of the through hole 130, the first annular groove 154 is in communication with the first oil guide groove 120, and is formed on the inner surface of the main bearing hub 122
  • the provision of the annular groove can further increase the oil supply between the main bearing hub 122 and the main shaft portion 102 of the crankshaft 10, thereby improving the lubrication condition of the main shaft portion 102 of the crankshaft 10.
  • the main bearing 12 due to the provision of the first annular groove 154, the main bearing 12 The contact area between the hub portion 122 and the main shaft portion 102 of the crankshaft 10 is reduced, thereby reducing the viscous resistance and friction loss between the two, thereby improving compressor performance.
  • the pump body assembly 1 further includes: an oil passage 156, the oil passage 156 is disposed in the first annular groove 154, and the oil passage 156 radially penetrates the hub portion 122 .
  • the oil passage 156 by arranging the oil passage 156 in the first annular groove 154, the oil passage 156 radially penetrates the hub portion 122, which can increase the fluidity between the lubricating oil on the inner surface of the hub and the external lubricating oil to a certain extent. The temperature of the lubricating oil in the hub is reduced, thereby further improving the lubrication reliability of the main shaft portion 102 of the crankshaft 10.
  • the radial depth of the first annular groove 154 of the pump body assembly 1 is less than or equal to 0.5 mm.
  • the radial depth of the first annular groove 154 is limited to no more than 0.5 mm, which ensures that the first annular groove 154 has a small effect on the rigidity of the entire pump body assembly 1.
  • the pump body assembly 1 further includes: a second annular groove 162, the second annular groove 162 is provided on the main shaft portion 102, the main shaft portion 102 and the hub portion 122 are matched Area.
  • the second annular groove 162 is provided on the main shaft portion 102 in the area where the main shaft portion 102 and the hub portion 122 fit.
  • the oil supply between the hub 122 of the main bearing 12 and the main shaft 102 of the crankshaft 10 can be further increased, thereby improving the lubrication of the main shaft 102 of the crankshaft 10.
  • the main bearing 12 due to the second annular groove 162, the main bearing 12 The contact area between the hub portion 122 and the main shaft portion 102 of the crankshaft 10 is reduced, thereby reducing the viscous resistance and friction loss between the two, thereby improving compressor performance.
  • the radial depth of the second annular groove 162 of the pump body assembly 1 is less than or equal to 0.5 mm.
  • the radial depth of the second annular groove 162 is limited to no more than 0.5 mm, which ensures the overall rigidity of the crankshaft, thereby ensuring that the second annular groove 162 has a small effect on the rigidity of the entire pump body assembly 1.
  • the crankshaft 10 of the pump body assembly 1 further includes a secondary shaft portion 106, and the eccentric portion 104 is located between the primary shaft portion 102 and the secondary shaft portion 106;
  • the pump body assembly 1 further includes a secondary bearing, and a main bearing sleeve It is arranged on the main shaft 102, and the auxiliary bearing is sleeved on the auxiliary shaft 106;
  • the pump body assembly 1 further includes: a second oil guide groove (not shown in the figure), the second oil guide groove is arranged in the through hole 130 of the auxiliary bearing .
  • the crankshaft 10 further includes a secondary shaft portion 106 connected to the eccentric portion 104.
  • the bearing includes a main bearing 12 and a secondary bearing.
  • the main bearing 12 and the secondary bearing are respectively located on two sides of the cylinder block 142.
  • the main bearing 12 is matched with the main shaft portion 102
  • the auxiliary bearing is matched with the auxiliary shaft portion 106
  • a first oil guide groove 120 is provided in the main bearing through hole
  • a second oil guide groove is provided in the auxiliary bearing through hole.
  • the lubricating oil is introduced between the main bearing and the main shaft portion 102 and between the auxiliary bearing and the auxiliary shaft portion 106, thereby The lubrication conditions of the main shaft portion 102 and the counter shaft portion 106 of the crankshaft 10 are improved.
  • the pump body assembly 1 further includes: a first connecting line 126 and a second oil guide groove between the center of the center hole 146 and the center of the sliding plate groove 144 in the same projection plane are in the hub portion
  • the value range of the included angle formed by the fourth connecting line between the end point of 122 near the end of the eccentric portion 104 and the center of the through hole 130 is less than or equal to 2 ⁇ and greater than or equal to 3 ⁇ /2.
  • the second oil guide groove forms a fourth line from the end point of the end of the hub portion 122 near the eccentric portion 104 to the center of the through hole 130, when The value range of the included angle formed by the first connecting line 126 and the fourth connecting line is less than or equal to 2 ⁇ and greater than or equal to 3 ⁇ /2, when the crankshaft 10 is deformed under the action of an external load and contacts the auxiliary bearing, the oil tank supplies more oil. Sufficient, the overall reliability of the crankshaft is better.
  • the first oil guide groove 120 and the second oil guide groove of the pump body assembly 1 are both spiral oil guide grooves.
  • the flow of lubricating oil is facilitated during the operation of the compressor, so that the inner wall surfaces of the main bearing 12 and the auxiliary bearing are in the spiral guide Under the action of the oil groove, lubricating oil is supplied to the main shaft portion 102 and the counter shaft portion 106 of the crankshaft 10, thereby achieving the effect of lubricating the main shaft portion 102 and the counter shaft portion 106 of the crankshaft 10.
  • the spiral direction of the first oil guide groove 120 and the second oil guide groove of the pump body assembly 1 is the same as the rotation direction of the crankshaft 10.
  • the spiral direction of the first oil guide groove 120 and the spiral direction of the second oil guide groove are the same as the rotation direction of the crankshaft 10, so that the lubricating oil can better enter the first oil guide groove 120 and the second oil guide groove 120 under the action of centrifugal force.
  • the oil guide groove increases the amount of oil supplied between the hub of the main bearing 12 and the shaft of the crankshaft 10.
  • the spiral direction of the first oil guide groove 120 and the spiral direction of the second oil guide groove are the same to ensure that the lubricating oil is introduced into the crankshaft 10 to contact the hub 122 Various locations.
  • the value range of the width of the first oil guide groove 120 of the pump body assembly 1 is less than or equal to 5 mm and greater than or equal to 1.5 mm; the value range of the depth of the first oil guide groove 120 is less than or equal to 3mm, and greater than or equal to 0.3mm.
  • connection line between the center of the cylinder block 142 and the center of the sliding plate groove 144 points to the direction of the sliding plate groove 144 as a 0° angle direction.
  • the angle increasing direction is the same as the crankshaft rotation direction 150. Unless otherwise specified, all angles are based on this.
  • M is the center point of the cylinder block 142
  • N is the center point of the piston 158
  • A is the tangent point of the piston 158 and the sliding plate 160 (for simplicity, the following calculation ignores the swing of the tangent point A, but the error is relatively large.
  • B is the tangent point between the piston 158 and the cylinder block 142
  • ⁇ is the crank angle
  • ⁇ is the direction angle of the gas force
  • ⁇ is the angle between AM and AN
  • ⁇ is the angle between AN and AB
  • r is The outer radius of the piston 158
  • e is the crankshaft eccentricity
  • the actual movement direction angle of the crankshaft 10 under the action of gas force is about ⁇ /6 ahead of the gas force direction angle ⁇ , so the actual movement direction angle of the crankshaft 10 is:
  • the discharge angle is usually (the corresponding crankshaft 10 rotation angle when the refrigerant starts to be discharged after compression) is around 7 ⁇ /6, and the formula (7 ) In ⁇ , get the direction angle of crankshaft movement corresponding to exhaust angle:
  • the optimal range of ⁇ - ⁇ d difference is - ⁇ /12 ⁇ - ⁇ d ⁇ 5 ⁇ /36, at this time, the range of oil tank termination angle ⁇ is:
  • the optimal range of ⁇ - ⁇ d difference is -5 ⁇ /36 ⁇ - ⁇ d ⁇ /36, and the end angle of the oil groove
  • the range of ⁇ is:
  • the gas force will have multiple peaks during a crankshaft rotation of 10 degrees, and the balance weight orientation (corresponding to the direction of centrifugal force) is quite different from that of a single cylinder.
  • the cylinders are not exactly the same.
  • the first oil guide groove 120 of the main bearing 12 is a spiral oil guide groove, and the rotation direction of the spiral oil guide groove is consistent with the rotation direction of the crankshaft 10.
  • the angle ⁇ 0 of the first oil guide groove 120 of the main bearing 12 close to the end point of the cylinder 142 also has a greater impact on the reliability of the main shaft portion 102 of the crankshaft 10.
  • the second oil guide groove of the auxiliary bearing is close to the starting angle of the cylinder 142 side Value At this time, the secondary shaft portion 106 has better reliability.
  • the width a and depth b of the first oil guide groove 120 also have a greater impact on the reliability of lubrication.
  • the width a of the first oil guide groove 120 ranges from 1.5mm ⁇ a ⁇ 5mm and the depth b ranges from 0.3mm ⁇ b ⁇ 3mm, the crankshaft 10 The overall reliability is better.
  • oil groove angle mentioned in this embodiment all refers to the angle between the end point of the first oil guide groove 120 and the center of the main bearing 12 and the angle of 0°.
  • the inner surface of the hub of the main bearing 12 is provided with a first annular groove 154, and the radial depth dimension of the first annular groove 154 is not greater than 0.5 mm.
  • An annular groove 154 the contact area between the main bearing hub 122 and the crankshaft 10 shaft portion is reduced, thereby reducing the viscous resistance and friction loss between the two, thereby improving compressor performance; limiting the diameter of the first annular groove 154
  • the depth dimension is not greater than 0.5 mm, which ensures that the first annular groove 154 has a small effect on the rigidity of the entire pump body assembly 1.
  • the second annular groove 162 is provided on the main shaft portion 102 of the crankshaft 10, and the area in contact with the hub portion 122 of the main bearing also ensures the second annular groove 162
  • the depth is not greater than 0.5 mm, and the principle is similar to that of providing an annular groove on the inner surface of the hub portion 122 of the main bearing 12, and will not be repeated here.
  • a radial oil passing hole 156 is added to the hub of the main bearing 12, which penetrates the inner and outer surfaces of the hub 122, and the oil passing hole 156 is located in the first annular groove 154 area.
  • the application of the present application to the rolling piston compressor is described in detail, but obviously, the present application is not limited to the rolling piston compressor, for example, for a rocking structure with integrated piston and sliding vanes (as shown in Figure 10 ) Or the hinged structure of the piston 158 and the sliding plate 160 (as shown in FIG. 11), this application can still be applied, and there is not much difference in the implementation mode.
  • the above-mentioned line is directed to the sliding plate with the center of the cylinder block 142 and the sliding plate groove 144
  • the direction of the fin groove 144 is the 0° angle direction.
  • the embodiment according to the second aspect of the present application provides a compressor, which includes the pump body assembly 1 as in any of the above embodiments. Therefore, it has all the beneficial effects of the pump body assembly 1, which will not be repeated here.
  • An embodiment according to the third aspect of the present application provides an air conditioner, which includes the pump body assembly 1 or the compressor as in any of the above embodiments. Therefore, it has all the beneficial effects of the pump body assembly 1 or the compressor, which will not be repeated here.
  • the term “plurality” refers to two or more than two, unless specifically defined otherwise.
  • the terms “installed”, “connected”, “connected”, “fixed” and other terms should be understood in a broad sense.
  • “connected” can be a fixed connection, a detachable connection, or an integral connection;
  • “connected” can be It is directly connected or indirectly connected through an intermediary.
  • the specific meanings of the above terms in this application can be understood according to specific circumstances.

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Abstract

一种泵体组件（1）、压缩机和空调器，泵体组件（1）包括：曲轴（10），曲轴（10）包括主轴部（102）和与其连接的偏心部（104），主轴部（102）的中心线和偏心部（104）的中心线之间的距离为e；主轴承（12），包括轮毂部（122），主轴部（102）穿设于轮毂部（122）的通孔（130），其孔壁上设置第一导油槽（120）；缸体（142），其上设置有滑片槽（144）和中心孔（146），曲轴（10）穿设于中心孔（146），主轴承（12）位于缸体（142）的两侧，中心孔（146）的半径为R，R与e的差值为r；其中，设置在同一投影面内的中心孔（146）的中心与滑片槽（144）的中心之间的第一连线（126）与第一导油槽（120）在轮毂部（122）远离偏心部（104）的一端的终止点至通孔（130）的中心之间的第二连线（128）构成的夹角的取值范围为：式（I），使曲轴（10）和主轴承（12）接触各处油膜更均匀，从而有效改善曲轴（10）主轴部（102）的异常磨损问题，提高压缩机的使用寿命。

Description

泵体组件、压缩机和空调器
本申请要求于2019年06月28日提交中国专利局、申请号为“2019105769338”、发明名称为“泵体组件、压缩机和空调器”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及压缩机技术领域，具体而言，涉及一种泵体组件、压缩机和空调器。
背景技术
目前，相关技术中压缩机泵体的曲轴润滑一般是通过在曲轴副轴下部内孔安装的螺旋的上油叶片供油。曲轴的主轴部和副轴部润滑主要通过在主轴承和副轴承内孔设置导油槽供油。导油槽的尺寸和位置设计是影响曲轴润滑的重要因素，若设计不当，会导致压缩机运转时曲轴主轴部供油不足，造成曲轴和主轴承磨损加剧，严重时甚至出现泵体卡死、曲轴断裂等问题，从而影响压缩机的使用寿命。
发明内容
本申请旨在至少解决现有技术或相关技术中存在的技术问题之一。
为此，本申请的第一个方面提出一种泵体组件。
本申请的第二个方面提出一种压缩机。
本申请第三个方面提出了一种空调器。
有鉴于此，根据本申请的一个方面，提供了一种泵体组件，包括：曲轴，曲轴包括：主轴部和与主轴部相连接的偏心部，主轴部的中心线和偏心部的中心线之间的距离为e；主轴承，主轴承包括轮毂部，主轴部穿设于轮毂部的通孔，通孔的孔壁上设置有第一导油槽；缸体，缸体上设置有滑片槽和中心孔，曲轴穿设于中心孔，主轴承位于缸体的一侧，中心孔的半径为R，R与e的差值为r；其中，在同一投影面内的中心孔的中心与滑片槽的 中心之间的第一连线与第一导油槽在轮毂部远离偏心部的一端的终止点至通孔的中心之间的第二连线构成的夹角的取值范围为小于等于17π/18与
Figure PCTCN2019109666-appb-000001
之和，且大于等于5π/9与
Figure PCTCN2019109666-appb-000002
之和，泵体组件的夹角为自第一连线沿曲轴的转动方向转动至第二连线所对应的转动角度。
本申请提供的泵体组件，包括：曲轴、主轴承和缸体，曲轴包括：主轴部和偏心部，主轴部和偏心部相连接，主轴部的中心线和偏心部的中心线之间具有偏心距离e；主轴承包括轮毂部，轮毂部上设有通孔，通孔的孔壁上设置有第一导油槽，主轴部穿过通孔；缸体上设置有中心孔和与中心孔相连通的滑片槽，曲轴穿过缸体的中心孔，缸体的一侧设置主轴承，中心孔的半径为R，r＝R-e；其中，在沿中心孔的轴线方向的同一投影面内，中心孔的中心与滑片槽的中心相连构成第一连线，第一导油槽在远离偏心部的一端的终止点与轮毂部的通孔的中心相连构成第二连线，在沿中心孔的轴线方向的同一投影面内，定义缸体中心孔的中心与滑片槽的中心之间的第一连线为0°方向，角度增加方向与曲轴转动方向相同，第一连线沿曲轴的转动方向转动至第二连线对应的角为夹角，夹角满足关系式：
Figure PCTCN2019109666-appb-000003
本申请通过限定在沿中心孔的轴线方向的同一投影面内的中心孔的中心与滑片槽的中心之间的第一连线与第一导油槽在轮毂部远离偏心部的一端的终止点至通孔的中心之间的第二连线构成的夹角、曲轴偏心量e和缸体的中心孔半径R的关系，使曲轴在外载荷作用下发生变形而与主轴承接触时，油槽供油更充分，曲轴主轴部各处油膜更均匀，从而有效改善曲轴主轴部的异常磨损问题，避免出现泵体卡死、曲轴断裂等问题，提高压缩机的使用寿命。
另外，根据本申请提供的上述技术方案中的泵体组件，还可以具有如下附加技术特征：
在上述技术方案中，泵体组件的缸体的数量为一个，夹角的取值范围为小于等于8π/9与
Figure PCTCN2019109666-appb-000004
之和，且大于等于2π/3与
Figure PCTCN2019109666-appb-000005
之和。
在该技术方案中，当泵体组件为单缸泵体组件时，夹角取值范围满足 公式：
Figure PCTCN2019109666-appb-000006
使曲轴在外载荷作用下发生变形而和主轴承接触时，油槽供油更充分。
在上述任一技术方案中，泵体组件的缸体的数量为至少两个，夹角的取值范围为小于等于7π/9与
Figure PCTCN2019109666-appb-000007
之和，且大于等于11π/18与
Figure PCTCN2019109666-appb-000008
之和。
在该技术方案中，泵体组件为多缸泵体组件时，夹角取值范围满足公式：
Figure PCTCN2019109666-appb-000009
使曲轴在外载荷作用下发生变形而和主轴承接触时，油槽供油更充分。进一步地，多缸压缩机在曲轴转角一周过程中，气体力会出现多个峰值，且平衡块方位(对应离心力方向)与单缸压缩机有较大不同，导致多缸压缩机油槽终止角最优范围与单缸不完全一致，通过根据缸体数量不同，设置油槽的位置不同，进而实现最佳的润滑效果。
在上述任一技术方案中，泵体组件在同一投影面内的第一连线与第一导油槽的另一端的终止点至通孔的中心之间的第三连线构成的夹角的取值范围为小于等于2π，且大于等于3π/2。
在该技术方案中，第一导油槽的另一端的终止点至通孔的中心构成第三连线，第一连线与第三连线构成的夹角对曲轴的可靠性影响较大，通过将第一连线与第三连线构成的夹角的取值范围设置为小于等于2π，且大于等于3π/2时，曲轴在外载荷作用下发生变形而和主轴承接触时，油槽供油更充分，曲轴的主轴部的可靠性较优。
在上述任一技术方案中，泵体组件还包括：第一环形槽，第一环形槽设置于通孔的孔壁上，第一导油槽与第一环形槽相连通。
在该技术方案中，泵体组件还包括设置于通孔孔壁上的第一环形槽，第一环形槽与第一导油槽相连通，通过在主轴承轮毂部内表面设置环形槽，可进一步增大主轴承轮毂部与曲轴主轴部之间的供油量，从而改善曲轴主轴部的润滑状况，同时，由于设置第一环形槽，主轴承的轮毂部与曲轴主轴部之间接触面积减小，从而减小二者之间的粘滞阻力和摩擦损失，从而提高压缩机性能。
在上述任一技术方案中，泵体组件还包括：过油孔，过油孔设置于第一 环形槽内，过油孔径向贯穿轮毂部。
在该技术方案中，通过在第一环形槽内设置过油孔，过油孔径向贯穿轮毂部，可增加轮毂内表面润滑油与外部润滑油之间流通性，一定程度上降低轮毂内润滑油温度，从而进一步提高曲轴主轴部润滑可靠性。
在上述任一技术方案中，泵体组件的第一环形槽的径向深度小于等于0.5mm。
在该技术方案中，限定第一环形槽径向深度不大于0.5mm，确保第一环形槽对于整个泵体组件刚性影响较小。
在上述技术方案中，泵体组件还包括：第二环形槽，第二环形槽设置于主轴部上，位于主轴部与轮毂部相配合的区域。
在该技术方案中，通过在主轴部与轮毂部相配合的区域上设置第二环形槽，可进一步增大主轴承轮毂部与曲轴主轴部之间的供油量，从而改善曲轴主轴部的润滑状况，同时，由于设置第二环形槽，主轴承的轮毂部与曲轴主轴部之间接触面积减小，从而减小二者之间的粘滞阻力和摩擦损失，从而提高压缩机性能。
在上述任一技术方案中，泵体组件的第二环形槽的径向深度小于等于0.5mm。
在该技术方案中，限定第二环形槽径向深度不大于0.5mm，保证了曲轴的整体刚度，进而确保第二环形槽对于整个泵体组件刚性影响较小。
在上述任一技术方案中，泵体组件的曲轴还包括副轴部，偏心部位于主轴部和副轴部之间；泵体组件还包括副轴承，主轴承套设在主轴部上，副轴承套设在副轴部上；泵体组件还包括：第二导油槽，第二导油槽设置于副轴承的通孔内。
在该技术方案中，曲轴还包括副轴部，与偏心部相连接，轴承包括主轴承和副轴承，主轴承和副轴承分别位于缸体的两侧，主轴承与主轴部配合，副轴承与副轴部配合，主轴承设置第一导油槽，副轴承通孔内设置第二导油槽。通过在主轴承通孔内设置第一导油槽，副轴承通孔内设置第二导油槽，使润滑油导入主轴承与主轴部之间，以及副轴承与副轴部之间，从而改善曲轴主轴部和副轴部的润滑状况。
在上述任一技术方案中，泵体组件还包括：在同一投影面内的中心孔的中心与滑片槽的中心之间的第一连线与第二导油槽在轮毂部靠近偏心部的一端的终止点至通孔的中心之间的第四连线构成的夹角的取值范围为小于等于2π，且大于等于3π/2。
在该技术方案中，在沿中心孔的轴线方向的同一投影面内，第二导油槽在轮毂部靠近偏心部的一端的终止点至通孔的中心构成第四连线，当第一连线与第四连线构成的夹角的取值范围为小于等于2π，且大于等于3π/2时，曲轴在外载荷作用下发生变形而和副轴承接触时，油槽供油更充分，曲轴整体可靠性较优。
在上述任一技术方案中，泵体组件的第一导油槽和第二导油槽均为螺旋导油槽。
在该技术方案中，通过将第一导油槽和第二导油槽设置为螺旋导油槽，在压缩机运转过程中有利于润滑油的流动，使主轴承和副轴承的内壁面在螺旋导油槽的作用下，将润滑油供给到曲轴主轴部和副轴部，从而起到对曲轴主轴部和副轴部润滑的效果。
在上述技术方案中，泵体组件的第一导油槽和第二导油槽的螺旋方向与曲轴的转动方向相同。
在该技术方案中，第一导油槽的螺旋方向和第二导油槽的螺旋方向与曲轴的转动方向相同，可以使润滑油在离心力作用下更好的进入第一导油槽和第二导油槽，增大主轴承轮毂与曲轴轴部之间的供油量，第一导油槽的螺旋方向和第二导油槽的螺旋方向相同，保证润滑油导入曲轴与轮毂部接触的各个位置。
在上述任一技术方案中，泵体组件的第一导油槽的宽度的取值范围为小于等于5mm，且大于等于1.5mm；第一导油槽的深度的取值范围为小于等于3mm，且大于等于0.3mm。
在该技术方案中，当第一导油槽宽度的取值范围为1.5mm≤第一导油槽宽度≤5mm，第一导油槽深度取值范围为0.3mm≤第一导油槽深度≤3mm时，曲轴的润滑可靠性较优。
根据本申请的第二个方面，提供了一种压缩机，包含上述任一技术方 案的泵体组件。因此具有该泵体组件的全部有益效果，在此不再赘述。
根据本申请的第三个方面，提供了一种空调器，包括上述任一技术方案的泵体组件或压缩机。因此具有该泵体组件或压缩机的全部有益效果，在此不再赘述。
本申请的附加方面和优点将在下面的描述部分中变得明显，或通过本申请的实践了解到。
附图说明
本申请的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1示出了现有技术中的泵体组件结构示意图。
其中，图1中附图标记与部件名称之间的对应关系为：
10’曲轴，102’主轴部，104’偏心部，106’副轴部，108’副轴油孔，110’油孔，112’上油叶片，122’主轴承轮毂，124’主轴承法兰，132’副轴承轮毂，134’副轴承法兰，142’缸体。
图2示出了根据本申请的一个实施例中的缸体结构示意图；
图3示出了根据本申请的一个实施例中的泵体组件运行时尺寸角度示意图；
图4示出了根据本申请的一个实施例中的泵体组件的主轴承的第一导油槽的远离气缸侧的终止角的示意图；
图5示出了根据本申请的又一个实施例中的泵体组件的主轴承的第一导油槽的靠近气缸侧的终止角的示意图；
图6示出了根据本申请的一个实施例中的泵体组件的第一导油槽的尺寸结构示意图；
图7示出了根据本申请的一个实施例中的轴承结构示意图；
图8示出了根据本申请的一个实施例中的曲轴结构示意图；
图9示出了根据本申请的又一个实施例中的轴承结构示意图；
图10示出了根据本申请的一个实施例中的摇摆式压缩机缸体结构示意图；
图11示出了根据本申请的一个实施例中的活塞滑片铰接结构示意图；
图12示出了根据本申请的一个实施例中的单缸压缩机夹角与曲轴磨损量关系图；
图13示出了根据本申请的一个实施例中的多缸压缩机夹角与曲轴磨损量关系图。
其中，图2至图11中附图标记与部件名称之间的对应关系为：
1泵体组件，10曲轴，102主轴部，104偏心部，106副轴部，12主轴承，120第一导油槽，122轮毂部，124法兰部，126第一连线，128第二连线，130通孔，142缸体，144滑片槽，146中心孔，150曲轴转动方向，152第三连线，154第一环形槽，156过油孔，158活塞，160滑片，162第二环形槽。
具体实施方式
为了能够更清楚地理解本申请的上述目的、特征和优点，下面结合附图和具体实施方式对本申请进行进一步的详细描述。需要说明的是，在不冲突的情况下，本申请的实施例及实施例中的特征可以相互组合。
在下面的描述中阐述了很多具体细节以便于充分理解本申请，但是，本申请还可以采用其他不同于在此描述的其他方式来实施，因此，本申请的保护范围并不受下面公开的具体实施例的限制。
下面参照图2至图13描述根据本申请一些实施例的泵体组件1、压缩机及空调器。
根据本申请的一个实施例提供了一种泵体组件1，包括：曲轴10，曲轴10包括：主轴部102和与主轴部102相连接的偏心部104，主轴部102的中心线和偏心部104的中心线之间的距离为e；主轴承12，主轴承12包括轮毂部122，主轴部102穿设于轮毂部122的通孔130，通孔130的孔壁上设置有第一导油槽120；缸体142，缸体142上设置有滑片槽144和中心孔146，曲轴10穿设于中心孔146，主轴承12位于缸体142的一侧，中心孔146的半径为R，R与e的差值为r；其中，在同一投影面内的中心孔146的中心与滑片槽144的中心之间的第一连线126与第一导油槽120在轮毂 部122远离偏心部104的一端的终止点至通孔130的中心之间的第二连线128构成的夹角的取值范围为小于等于17π/18与
Figure PCTCN2019109666-appb-000010
之和，且大于等于5π/9与
Figure PCTCN2019109666-appb-000011
之和。
如图4所示，本申请提供的泵体组件1，包括：曲轴10、主轴承12和缸体142，曲轴10包括：主轴部102和偏心部104，主轴部102和偏心部104相连接，主轴部102的中心线和偏心部104的中心线之间具有偏心距离e；主轴承12包括轮毂部122和法兰部124，轮毂部122上设有通孔130，通孔130的孔壁上设置有第一导油槽120，主轴部102穿过通孔130；缸体142上设置有中心孔146和与中心孔146相连通的滑片槽144，曲轴10穿过缸体142的中心孔146，缸体142的两侧设置主轴承12，中心孔146的半径为R，r＝R-e；其中，在沿中心孔146的轴线方向的同一投影面内，定义缸体142中心孔146的中心与滑片槽144的中心之间的第一连线126为0°方向，中心孔146的中心与滑片槽144的中心相连构成第一连线126，第一导油槽120在远离偏心部104的一端的终止点与轮毂部122的通孔130的中心相连构成第二连线128，角度增加方向与曲轴转动方向150相同，第一连线126沿曲轴10的转动方向转动至第二连线128对应的角为夹角，夹角满足关系式：
Figure PCTCN2019109666-appb-000012
本申请通过限定在沿中心孔的轴线方向的同一投影面内的中心孔146的中心与滑片槽144的中心之间的第一连线126与第一导油槽120在轮毂部122远离偏心部104的一端的终止点至通孔130的中心之间的第二连线128构成的夹角、曲轴10偏心量e和缸体142的中心孔146半径R的关系，使曲轴10在外载荷作用下发生变形而与主轴承12接触时，油槽供油更充分，曲轴10主轴部102各处油膜更均匀，从而有效改善曲轴10主轴部102的异常磨损问题，避免出现泵体卡死、曲轴断裂等问题，提高压缩机的使用寿命。
下面结合图1对现有结构压缩机曲轴润滑原理及磨损机理进行简要分析说明：
如图1所示，压缩机泵体组件包括：曲轴10’、轴承及缸体142’。其中，曲轴10’包括：主轴部102’、偏心部104’、副轴部106’；轴承 包括主轴承和副轴承，主轴承包括主轴承轮廓122’和主轴承法兰124’，主轴部102’设置于主轴承轮廓122’处，副轴承包括副轴承轮毂132’和副轴承法兰134’，副轴部106’设置于副轴承轮毂132’处，曲轴10’润滑一般是通过在10’的副轴部106’内孔安装的螺旋的上油叶片112’供油，曲轴10’转动时，上油叶片112’将压缩机油池底部的润滑油往上供油，通过曲轴10’的主轴部102’和副轴部106’的油孔110’传递到主轴承内孔和副轴承内孔，紧接着在主副轴承内壁面螺旋导油槽的作用下，将润滑油供给到曲轴主轴部102’和副轴部106’，从而起到对曲轴10’的主轴部102’和副轴部106’润滑的效果。压缩机运转时，曲轴10’受到气体力、径向磁拉力和平衡块离心力作用，作用力导致曲轴10’变形而产生倾斜，与轴承接触而产生接触应力。倘若接触应力过大，或轴承导油槽位置设置不合理，将导致曲轴由于供油不充足而与轴承发生异常磨损。
本申请基于以上曲轴润滑原理及磨损机理，结合曲轴的受力情况，对主轴承的导油槽终止点与曲轴偏心量、缸体142半径等之间的关系进行了深入分析研究，提出了一种新的主轴承12为螺旋导油槽设计结构，实施简单，效果显著，需要说明的是，本申请的结构对于不同冷媒及润滑油压缩机均适用。
在本申请的一个实施例中，泵体组件1的缸体142的数量为一个，夹角的取值范围为小于等于8π/9与
Figure PCTCN2019109666-appb-000013
之和，且大于等于2π/3与
Figure PCTCN2019109666-appb-000014
之和。
在该实施例中，当泵体组件1为单缸泵体组件时，夹角取值范围满足公式：
Figure PCTCN2019109666-appb-000015
使曲轴10在外载荷作用下发生变形而和主轴承12接触时，油槽供油更充分。
在本申请的一个实施例中，泵体组件1的缸体142的数量为至少两个，夹角的取值范围为小于等于7π/9与
Figure PCTCN2019109666-appb-000016
之和，且大于等于11π/18与
Figure PCTCN2019109666-appb-000017
之和。
在该实施例中，泵体组件1为多缸泵体组件时，夹角取值范围满足公式：
Figure PCTCN2019109666-appb-000018
使曲轴10在外载荷作用下 发生变形而和主轴承12接触时，油槽供油更充分。进一步地，多缸压缩机在曲轴转角一周过程中，气体力会出现多个峰值，且平衡块方位(对应离心力方向)与单缸压缩机有较大不同，导致多缸压缩机油槽终止角最优范围与单缸不完全一致，通过根据缸体数量不同，设置油槽的位置不同，进而实现最佳的润滑效果。
在本申请的一个实施例中，如图5所示，泵体组件1在同一投影面内的第一连线126与第一导油槽120的另一端的终止点至通孔130的中心之间的第三连线152构成的夹角的取值范围为小于等于2π，且大于等于3π/2。
在该实施例中，第一导油槽120的另一端的终止点至通孔130的中心构成第三连线152，第一连线126与第三连线152构成的夹角对曲轴10的可靠性影响较大，通过将第一连线126与第三连线152构成的夹角的取值范围为小于等于2π，且大于等于3π/2时，曲轴10在外载荷作用下发生变形而和主轴承12接触时，油槽供油更充分，曲轴10的主轴部102的可靠性较优。
在本申请的一个实施例中，如图7所示，泵体组件1还包括：第一环形槽154，第一环形槽154设置于通孔130的孔壁上，第一导油槽120与第一环形槽154相连通。
在该实施例中，泵体组件1还包括设置于通孔130孔壁上的第一环形槽154，第一环形槽154与第一导油槽120相连通，通过在主轴承轮毂部122内表面设置环形槽，可进一步增大主轴承轮毂部122与曲轴10主轴部102之间的供油量，从而改善曲轴10主轴部102的润滑状况，同时，由于设置第一环形槽154，主轴承12的轮毂部122与曲轴10的主轴部102之间接触面积减小，从而减小二者之间的粘滞阻力和摩擦损失，从而提高压缩机性能。
在本申请的一个实施例中，如图9所示，泵体组件1还包括：过油孔156，过油孔156设置于第一环形槽154内，过油孔156径向贯穿轮毂部122。
在该实施例中，通过在第一环形槽154内设置过油孔156，过油孔156径向贯穿轮毂部122，可增加轮毂内表面润滑油与外部润滑油之间流通性，一定程度上降低轮毂内润滑油温度，从而进一步提高曲轴10主轴部102润 滑可靠性。
在本申请的一个实施例中，泵体组件1的第一环形槽154的径向深度小于等于0.5mm。
在该实施例中，限定第一环形槽154径向深度不大于0.5mm，确保第一环形槽154对于整个泵体组件1刚性影响较小。
在本申请的一个实施例中，如图8所示，泵体组件1还包括：第二环形槽162，第二环形槽162设置于主轴部102上，位于主轴部102与轮毂部122相配合的区域。
在该实施例中，通过在主轴部102与轮毂部122相配合的区域上设置第二环形槽162，第二环形槽162设置于主轴部102与轮毂部122相配合的区域的主轴部102上，可进一步增大主轴承12的轮毂部122与曲轴10主轴部102之间的供油量，从而改善曲轴10主轴部102的润滑状况，同时，由于设置第二环形槽162，主轴承12的轮毂部122与曲轴10主轴部102之间接触面积减小，从而减小二者之间的粘滞阻力和摩擦损失，从而提高压缩机性能。
在本申请的一个实施例中，泵体组件1的第二环形槽162的径向深度小于等于0.5mm。
在该实施例中，限定第二环形槽162径向深度不大于0.5mm，保证了曲轴的整体刚度，进而确保第二环形槽162对于整个泵体组件1刚性影响较小。
在本申请的一个实施例中，泵体组件1的曲轴10还包括副轴部106，偏心部104位于主轴部102和副轴部106之间；泵体组件1还包括副轴承，主轴承套设在主轴部102上，副轴承套设在副轴部106上；泵体组件1还包括：第二导油槽(图中未示出)，第二导油槽设置于副轴承的通孔130内。
在该实施例中，如图8所示，曲轴10还包括副轴部106，与偏心部104相连接，轴承包括主轴承12和副轴承，主轴承12和副轴承分别位于缸体142的两侧，主轴承12与主轴部102配合，副轴承与副轴部106配合，主轴承通孔内设置第一导油槽120，副轴承通孔内设置第二导油槽。通过在主轴承通孔内设置第一导油槽120，副轴承通孔内设置第二导油槽，使润 滑油导入主轴承与主轴部102之间，以及副轴承与副轴部106之间，从而改善曲轴10的主轴部102和副轴部106的润滑状况。
在本申请的一个实施例中，泵体组件1还包括：在同一投影面内的中心孔146的中心与滑片槽144的中心之间的第一连线126与第二导油槽在轮毂部122靠近偏心部104的一端的终止点至通孔130的中心之间的第四连线构成的夹角的取值范围为小于等于2π，且大于等于3π/2。
在该实施例中，在沿中心孔146的轴线方向的同一投影面内，第二导油槽在轮毂部122靠近偏心部104的一端的终止点至通孔130的中心构成第四连线，当第一连线126与第四连线构成的夹角的取值范围为小于等于2π，且大于等于3π/2时，曲轴10在外载荷作用下发生变形而和副轴承接触时，油槽供油更充分，曲轴整体可靠性较优。
在本申请的一个实施例中，泵体组件1的第一导油槽120和第二导油槽均为螺旋导油槽。
在该实施例中，通过将第一导油槽120和第二导油槽设置为螺旋导油槽，在压缩机运转过程中有利于润滑油的流动，使主轴承12和副轴承的内壁面在螺旋导油槽的作用下，将润滑油供给到曲轴10的主轴部102和副轴部106，从而起到对曲轴10的主轴部102和副轴部106润滑的效果。
在本申请的一个实施例中，泵体组件1的第一导油槽120和第二导油槽的螺旋方向与曲轴10的转动方向相同。
在该实施例中，第一导油槽120的螺旋方向和第二导油槽的螺旋方向与曲轴10的转动方向相同，可以使润滑油在离心力作用下更好的进入第一导油槽120和第二导油槽，增大主轴承12轮毂与曲轴10轴部之间的供油量，第一导油槽120的螺旋方向和第二导油槽的螺旋方向相同，保证润滑油导入曲轴10与轮毂部122接触的各个位置。
在本申请的一个实施例中，泵体组件1的第一导油槽120的宽度的取值范围为小于等于5mm，且大于等于1.5mm；第一导油槽120的深度的取值范围为小于等于3mm，且大于等于0.3mm。
在该实施例中，如图6所示，当第一导油槽120宽度a的取值范围为1.5mm≤a≤5mm，第一导油槽120深度b取值范围为0.3mm≤b≤3mm时，曲 轴10的润滑可靠性较优。
具体的实施例中，定义气缸缸体142中心与滑片槽144中心连线指向滑片槽144方向为0°角方向，如图2所示，角度增加方向与曲轴转动方向150相同，后续若无特殊说明的话，所有角度均以此为基准。本实施例中，活塞158套设在曲轴10的偏心部104外侧，活塞158外半径尺寸为r＝R-e。
如图3所示，M为气缸缸体142中心点，N为活塞158中心点，A为活塞158与滑片160切点(简化起见，下述计算忽略了切点A的摆动，但误差较小)，B为活塞158与气缸缸体142切点，θ为曲轴转角，α为气体力合力方向角，β为AM与AN的夹角，δ为AN与AB之间的夹角，r为活塞158外半径，e为曲轴偏心量，则以上各角度尺寸满足以下几何关系式：
Figure PCTCN2019109666-appb-000019
故：
Figure PCTCN2019109666-appb-000020
又：θ-π＝2δ+β                                (3)
故：
Figure PCTCN2019109666-appb-000021
Figure PCTCN2019109666-appb-000022
综合公式(2)、(4)、(5)可得：
Figure PCTCN2019109666-appb-000023
根据主轴承12润滑相关计算，曲轴10在气体力作用下实际运动方向角度较气体力方向角α超前约π/6，故曲轴10实际运动方向角度为：
Figure PCTCN2019109666-appb-000024
对于现有压缩机机种，包括R22、R410A、R32、R290、R134a等冷媒，排气角通常(冷媒压缩后刚开始排气时对应的曲轴10转角)在7π/6附近，代入公式(7)中的θ，得到排气角对应的曲轴运动方向角度：
Figure PCTCN2019109666-appb-000025
排气时曲轴10受到的气体力达到最大值，曲轴10的径向运动达到最大，对主轴部102的润滑影响也达到最大。通过大量实验研究表明，曲轴10的主轴部102磨损量与主轴承远离气缸142侧油槽终止角度σ、排气角时曲轴10实际运动角度λ d之间有较大联系，具体可通过下图12表示，当σ-λ d差值在-7π/36到7π/36之间时，曲轴10主轴部102磨损量较小，此时曲轴10可靠性较高，将-7π/36≤σ-λ d≤7π/36代入公式(8)，即可得到主轴承12远离气缸侧油槽终止角度σ优选范围为：
Figure PCTCN2019109666-appb-000026
更，对于单缸泵体组件及单缸压缩机，σ-λ d的差值最优范围为-π/12<σ-λ d<5π/36，此时油槽终止角度σ范围为：
Figure PCTCN2019109666-appb-000027
更，对于多缸泵体组件及多缸压缩机，如图13所示，σ-λ d的差值最优范围为-5π/36<σ-λ d<π/36，此时油槽终止角度σ范围为：
Figure PCTCN2019109666-appb-000028
多缸压缩机在曲轴10转角一周过程中，气体力会出现多个峰值，且平衡块方位(对应离心力方向)与单缸有较大不同，导致多缸压缩机油槽终止角最优范围与单缸不完全一致。
具体实施例中，主轴承12的第一导油槽120为螺旋导油槽，且螺旋导油槽旋向与曲轴10的转动方向一致。
具体实施例中，如图5所示，主轴承12的第一导油槽120靠近气缸142侧终止点的角度σ 0范围对曲轴10的主轴部102可靠性影响同样较大，研究发现，3π/2≤σ 0≤2π时，曲轴10的主轴部102可靠性较优，同样的，副轴承的第二导油槽靠近气缸142侧起始角度
Figure PCTCN2019109666-appb-000029
取值
Figure PCTCN2019109666-appb-000030
时，副轴部106可靠性较优。
第一导油槽120的宽度a、深度b对润滑可靠性同样影响较大，当第一导油槽120宽度a范围为1.5mm≤a≤5mm，深度b范围为0.3mm≤b≤3mm时，曲轴10整体可靠性较优。
需要说明的是，本实施例中提到的油槽角度均指的是第一导油槽120的终止点与主轴承12中心连线与0°角之间的夹角。
本申请的一个实施例中，如图7所示，主轴承12轮毂内表面设有第一环形槽154，第一环形槽154径向深度尺寸不大于0.5mm。通过在主轴承12轮毂内表面设置第一环形槽154，可进一步增大主轴承12轮毂与曲轴10轴部之间的供油量，从而改善曲轴10轴部的润滑状况，同时，由于设置第一环形槽154，主轴承轮毂部122与曲轴10轴部之间接触面积减小，从而减小二者之间的粘滞阻力和摩擦损失，从而提高压缩机性能；限定第一环形槽154径向深度尺寸不大于0.5mm，确保第一环形槽154对于整个泵体组件1的刚性影响较小。
本申请的一个实施例中，如图8所示，将第二环形槽162设置在曲轴10的主轴部102上，与主轴承的轮毂部122部接触的区域，同样保证第二环形槽162的深度不大于0.5mm，其原理与在主轴承12的轮毂部122内表面设置环形槽类似，在此不再赘述。
本申请的一个实施例中，如图9所示，在主轴承12轮毂增加了径向过油孔156，贯穿轮毂部122的内外表面，且过油孔156位于第一环形槽154区域。通过设置径向贯穿的过油孔156，可增加轮毂部122内表面润滑油与外部润滑油之间流通性，一定程度上降低轮毂内润滑油温度，从而进一步提高曲轴10的轴部润滑可靠性。
以上实施例中，对本申请在滚动活塞式压缩机上的应用进行了详细说明，但显然本申请并不限制于滚动活塞式压缩机，比如对于活塞滑片一体的摇摆式结构(如图10所示)或活塞158与滑片160铰接结构(如图11所示)，本申请仍然可以应用，实施方式并无太大区别，上述均以气缸缸体142中心与滑片槽144中心连线指向滑片槽144方向为0°角方向，如果滑片槽144中心无法明显地确定时，定义气缸吸气腔与排气腔合为一个腔的时刻对应曲轴10转角为0°角，角度增加方向与曲轴转动方向150相同，此时主轴承12远离气缸侧油槽终止角度σ优选范围仍为：
Figure PCTCN2019109666-appb-000031
以上示意性的对本申请方案具体实施方式进行了阐述，具体实施时可在此基础上作相应的变化，而不应视为对本申请保护范围的限制。比如，以上实施例中主轴承12轮毂远离气缸侧终止角度σ限定为
Figure PCTCN2019109666-appb-000032
但对油槽数量、形状并无限定，即只要满足此角度要求的任意数量和形状的油槽，均认为在本专利的保护范围之内。
根据本申请的第二个方面的实施例提供了一种压缩机，压缩机包括如上述任一实施例中的泵体组件1。因此具有该泵体组件1的全部有益效果，在此不再赘述。
根据本申请的第三个方面的实施例提供了一种空调器，空调器包括如上述任一实施例中的泵体组件1或压缩机。因此具有该泵体组件1或压缩机的全部有益效果，在此不再赘述。
在本申请中，术语“多个”则指两个或两个以上，除非另有明确的限定。术语“安装”、“相连”、“连接”、“固定”等术语均应做广义理解，例如，“连接”可以是固定连接，也可以是可拆卸连接，或一体地连接；“相连”可以是直接相连，也可以通过中间媒介间接相连。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
在本说明书的描述中，术语“一个实施例”、“一些实施例”、“具体实施例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或实例。而且，描述的具体特征、结构、材料或特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
以上仅为本申请的优选实施例而已，并不用于限制本申请，对于本领域的技术人员来说，本申请可以有各种更改和变化。凡在本申请的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本申请的保护范围之内。

Claims (16)

  1. 一种泵体组件，其中，包括：
    曲轴，所述曲轴包括：主轴部和与所述主轴部相连接的偏心部，所述主轴部的中心线和所述偏心部的中心线之间的距离为e；
    主轴承，所述主轴承包括轮毂部，所述主轴部穿设于所述轮毂部的通孔，所述通孔的孔壁上设置有第一导油槽；
    缸体，所述缸体上设置有滑片槽和中心孔，所述曲轴穿设于所述中心孔，所述主轴承位于所述缸体的一侧，所述中心孔的半径为R，所述R与所述e的差值为r；
    其中，在同一投影面内的所述中心孔的中心与所述滑片槽的中心之间的第一连线与所述第一导油槽在所述轮毂部远离所述偏心部的一端的终止点至所述通孔的中心之间的第二连线构成的夹角的取值范围为小于等于17π/18与
    Figure PCTCN2019109666-appb-100001
    之和，且大于等于5π/9与
    Figure PCTCN2019109666-appb-100002
    之和；所述夹角为自所述第一连线沿所述曲轴的转动方向转动至所述第二连线所对应的转动角度。
  2. 根据权利要求1所述的泵体组件，其中，
    所述缸体的数量为一个，所述夹角的取值范围为小于等于8π/9与
    Figure PCTCN2019109666-appb-100003
    之和，且大于等于2π/3与
    Figure PCTCN2019109666-appb-100004
    之和。
  3. 根据权利要求2所述的泵体组件，其中，
    所述缸体的数量为至少两个，所述夹角的取值范围为小于等于7π/9与
    Figure PCTCN2019109666-appb-100005
    之和，且大于等于11π/18与
    Figure PCTCN2019109666-appb-100006
    之和。
  4. 根据权利要求1至3中任一项所述的泵体组件，其中，
    在同一投影面内的所述第一连线与所述第一导油槽的另一端的终止点至所述通孔的中心之间的第三连线构成的夹角的取值范围为小于等于2π，且大于等于3π/2。
  5. 根据权利要求1至4中任一项所述的泵体组件，其中，还包括：第一环形槽，所述第一环形槽设置于所述通孔的孔壁上，所述第一导油槽与所述第一环形槽相连通。
  6. 根据权利要求5所述的泵体组件，其中，还包括：
    过油孔，所述过油孔设置于所述第一环形槽内，所述过油孔径向贯穿所述轮毂部。
  7. 根据权利要求5所述的泵体组件，其中，
    所述第一环形槽的径向深度小于等于0.5mm。
  8. 根据权利要求1至7中任一项所述的泵体组件，其中，还包括：第二环形槽，所述第二环形槽设置于所述主轴部上，位于所述主轴部与所述轮毂部相配合的区域。
  9. 根据权利要求8所述的泵体组件，其中，
    所述第二环形槽的径向深度小于等于0.5mm。
  10. 根据权利要求1至9中任一项所述的泵体组件，其中，所述曲轴还包括副轴部，所述偏心部位于所述主轴部和所述副轴部之间；
    所述泵体组件还包括副轴承，所述主轴承套设在所述主轴部上，所述副轴承套设在所述副轴部上主轴承；
    所述泵体组件还包括：第二导油槽，所述第二导油槽设置于所述副轴承的通孔内。
  11. 根据权利要求10所述的泵体组件，其中，还包括：
    在所述同一投影面内的所述中心孔的中心与所述滑片槽的中心之间的第一连线与所述第二导油槽在所述轮毂部靠近所述偏心部的一端的终止点至所述通孔的中心之间的第四连线构成的夹角的取值范围为小于等于2π，且大于等于3π/2。
  12. 根据权利要求10所述的泵体组件，其中，
    所述第一导油槽和所述第二导油槽均为螺旋导油槽。
  13. 根据权利要求12所述的泵体组件，其中，
    所述第一导油槽和所述第二导油槽的螺旋方向与所述曲轴的转动方向相同。
  14. 根据权利要求1至13中任一项所述的泵体组件，其中，
    所述第一导油槽的宽度的取值范围为小于等于5mm，且大于等于1.5mm；
    所述第一导油槽的深度的取值范围为小于等于3mm，且大于等于0.3mm。
  15. 一种压缩机，其中，包括如权利要求1至14中任一项所述的泵体组件。
  16. 一种空调器，其中，包括如权利要求1至14中任一项所述的泵体组件；或
    如权利要求15所述的压缩机。
PCT/CN2019/109666 2019-06-28 2019-09-30 泵体组件、压缩机和空调器 WO2020258580A1 (zh)

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