EP4729783A1 - Rotary compressor and refrigeration apparatus - Google Patents

Rotary compressor and refrigeration apparatus

Info

Publication number
EP4729783A1
EP4729783A1 EP24845226.0A EP24845226A EP4729783A1 EP 4729783 A1 EP4729783 A1 EP 4729783A1 EP 24845226 A EP24845226 A EP 24845226A EP 4729783 A1 EP4729783 A1 EP 4729783A1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
oil
viewed
oil passage
axial direction
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.)
Pending
Application number
EP24845226.0A
Other languages
German (de)
French (fr)
Inventor
Taro KISHIMOTO
Masaaki Adachi
Tsuyoshi Fukunaga
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP4729783A1 publication Critical patent/EP4729783A1/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • 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
    • F04C18/322—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
    • F04C18/344—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
    • F04C18/356—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
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/025—Lubrication; Lubricant separation using a lubricant 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
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • F04C2240/40—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/60—Shafts
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
    • 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
    • F04C2240/605—Shaft sleeves 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
    • 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
    • F04C2240/806—Pipes for fluids; Fittings therefor
    • 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
    • F04C2240/807—Balance weight, counterweight
    • 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
    • F04C2240/809—Lubricant sump

Landscapes

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

Abstract

A drive shaft (25) has a main shaft portion (26) and an eccentric portion (27). The drive shaft (25) has an oil passage (30). The oil passage (30) includes one or more oil holes (31) extending in an axial direction. As viewed in the axial direction of the drive shaft (25), a predetermined direction in a region surrounded by a phantom envelope (40) that envelops the one or more oil holes (31) is referred to as a first direction (Y), and a direction orthogonal to the first direction (Y) is referred to as a second direction (X). As viewed in the axial direction, the oil passage (30) has a length in the first direction (Y) that is greater than a length in the second direction (X) in the region surrounded by the phantom envelope (40).

Description

    TECHNICAL FIELD
  • The present disclosure relates to a rotary compressor and a refrigeration apparatus.
    • BACKGROUND ART
  • Patent Document 1 discloses a compressor including: a compression mechanism having a rolling piston; and a drive shaft (shaft) that eccentrically rotates the rolling piston. The drive shaft has an oil passage (center hole) extending in an axial direction. Refrigerating machine oil stored at the bottom of a closed container is supplied through the oil passage to sliding portions.
    • CITATION LIST PATENT DOCUMENT
  • [Patent Document 1] Japanese Patent No. 7003305
    • SUMMARY OF THE INVENTION TECHNICAL PROBLEM
  • Here, centrifugal force and gas load are applied to the drive shaft as the compression mechanism is driven and rotates, resulting in an increase in the shaft deflection of the drive shaft.
  • To address this, the inventors of this application have focused on the oil passage that is a cause of lower rigidity of the drive shaft, and have studied how to increase the rigidity of the drive shaft through improvement in the shape of the oil passage.
  • An object of the present disclosure is to reduce shaft deflection of a drive shaft through improvement in the shape of an oil passage.
    • SOLUTION TO THE PROBLEM
  • A first aspect of the present disclosure is directed to a rotary compressor including: a compression mechanism (50); and a drive shaft (25) configured to rotationally drive the compression mechanism (50), the drive shaft (25) including a main shaft portion (26) and an eccentric portion (27), the eccentric portion (27) being eccentric with respect to an axis (C1) of the main shaft portion (26) by a predetermined distance, the drive shaft (25) having an oil passage (30) including one or more oil holes (31) extending in an axial direction, as viewed in the axial direction of the drive shaft (25), a predetermined direction in a region surrounded by a phantom envelope (40) that envelops the one or more oil holes (31) being referred to as a first direction (Y), a direction orthogonal to the first direction (Y) being referred to as a second direction (X), as viewed in the axial direction, the oil passage (30) has a length in the first direction (Y) that is greater than a length in the second direction (X) in the region surrounded by the phantom envelope (40).
  • According to the first aspect, the rigidity of the drive shaft (25) can be increased, thereby reducing shaft deflection, by forming the oil passage (30) such that the length in the first direction (Y) is greater than the length in the second direction (X) in the region surrounded by the phantom envelope (40).
  • Specifically, to suck up oil by centrifugal pumping action, a centrifugal pump needs to structurally include a small-diameter portion located near its inlet and a large-diameter portion located near its outlet, the large-diameter portion having a greater diameter than the small-diameter portion.
  • In known rotary compressors, the small-diameter portion of the centrifugal pump near the inlet corresponds to a tapered suction port that is open to a lower end portion of the centrifugal pump, and the large-diameter portion near the outlet corresponds to a circular oil passage extending in the axial direction through a central portion of the drive shaft (25). Thus, in known rotary compressors, a circular oil passage having a relatively large diameter corresponding to the length in the first direction (Y) is formed in the central portion of the drive shaft (25), which may reduce the rigidity of the drive shaft (25).
  • In contrast, by setting the length of the oil passage (30) in the second direction (X) to be shorter than the length in the first direction (Y), the area of the oil passage (30) can be made smaller than that of a circular oil passage provided at the central portion of the drive shaft (25), thereby improving the rigidity of the drive shaft (25) and reducing the shaft deflection.
  • Further, by setting the distance from the center of rotation of the drive shaft (25) to the inner wall surface of the oil passage (30) at a point farthest from the center of rotation in the radial direction to be equivalent to the radius of a circular oil passage, an equivalent centrifugal pumping action can be obtained.
  • A second aspect of the present disclosure is an embodiment of the rotary compressor of the first aspect. In the second aspect, the first direction (Y) is a direction that connects the axis (C1) of the main shaft portion (26) and an axis (C2) of the eccentric portion (27), as viewed in the axial direction of the drive shaft (25).
  • According to the second aspect, the rigidity of the drive shaft (25) in the second direction (X) is higher than the rigidity in the first direction (Y). Thus, the shaft deflection of the drive shaft (25) can be reduced even if the maximum gas load during the rotational driving of the compression mechanism (50) is applied to the drive shaft (25) in the second direction (X).
  • A third aspect of the present disclosure is an embodiment of the rotary compressor of the first or second aspect. In the third aspect, the oil passage (30) is formed as a long oil hole (31) extending along the first direction (Y) as viewed in the axial direction.
  • According to the third aspect, by forming the oil passage (30) as the long oil hole (31) extending along the first direction (Y) as viewed in the axial direction, the rigidity of the drive shaft (25) in the second direction (X) can be higher than the rigidity in the first direction (Y).
  • A fourth aspect of the present disclosure is an embodiment of the rotary compressor of the first or second aspect. In the fourth aspect, the oil passage (30) is formed by the plurality of oil holes (31) arranged along the first direction (Y) as viewed in the axial direction.
  • According to the fourth aspect, by forming the oil passage (30) as a plurality of oil holes (31) arranged along the first direction (Y), the rigidity of the drive shaft (25) in the second direction (X) can be higher than the rigidity in the first direction (Y).
  • A fifth aspect of the present disclosure is an embodiment of the rotary compressor of the fourth aspect. In the fifth aspect, in the oil passage (30), the plurality of oil holes (31) is arranged so that the oil holes (31) adjacent to each other partially overlap each other as viewed in the axial direction.
  • According to the fifth aspect, assuming that the length in the first direction (Y) of the region surrounded by the phantom envelope (40) is constant, the number of oil holes (31) in the region surrounded by the phantom envelope (40) is greater when adjacent oil holes (31) partially overlap with each other than when adjacent oil holes (31) are spaced apart from each other. Thus, machining the oil passage (30) into a long-hole shape becomes easier.
  • A sixth aspect of the present disclosure is an embodiment of the rotary compressor of any one of the first to fifth aspects, further including: a motor (21) configured to rotate the drive shaft (25), wherein the compression mechanism (50) is disposed below the motor (21).
  • According to the sixth aspect, the oil passage (30) having a shape in which the length in the first direction (Y) is greater than the length in the second direction (X) in the region surrounded by the phantom envelope (40) is applicable to a rotary compressor in which the compression mechanism (50) is arranged below the motor (21).
  • A seventh aspect of the present disclosure is directed to a refrigeration apparatus including: the rotary compressor (10) of any one of the first to sixth aspects; and a refrigerant circuit (1a) through which a refrigerant compressed by the rotary compressor (10) flows.
  • According to the seventh aspect, it is possible to provide a refrigeration apparatus including the rotary compressor (10) and the refrigerant circuit (1a).
    • BRIEF DESCRIPTION OF THE DRAWINGS
    • [FIG. 1] FIG. 1 is a refrigerant circuit diagram illustrating a configuration of a refrigeration apparatus according to a first embodiment.
    • [FIG. 2] FIG. 2 is a longitudinal sectional view illustrating a configuration of a rotary compressor.
    • [FIG. 3] FIG. 3 is a transverse sectional view illustrating the configuration of the rotary compressor.
    • [FIG. 4] FIG. 4 is a diagram illustrating a drive shaft as viewed in an axial direction.
    • [FIG. 5] FIG. 5 is a cross-sectional view of the drive shaft taken along line A-A shown in FIG. 2.
    • [FIG. 6] FIG. 6 is a diagram illustrating second moment of area in a situation where load is applied to a main shaft portion of the drive shaft in a first direction.
    • [FIG. 7] FIG. 7 is a diagram illustrating second moment of area in a situation where load is applied to a main shaft portion of the drive shaft in a second direction.
    • [FIG. 8] FIG. 8 is a graph showing the relationship between an angle from the top dead center and the magnitude of force applied to the drive shaft.
    • [FIG. 9] FIG. 9 is a graph showing the relationship between an angle from the top dead center and the direction of force applied to the drive shaft.
    • [FIG. 10] FIG. 10 is a graph showing the relationship between an angle from the top dead center, and the direction of force applied to the drive shaft when the direction of eccentricity of an eccentric portion is taken as a reference 0°.
    • [FIG. 11] FIG. 11 is a diagram illustrating the angle at which a maximum gas load is applied to the drive shaft.
    • [FIG. 12] FIG. 12 is a diagram illustrating a drive shaft of a second embodiment as viewed in an axial direction.
    • [FIG. 13] FIG. 13 is a diagram illustrating a drive shaft of a third embodiment as viewed in an axial direction.
    • [FIG. 14] FIG. 14 is a diagram illustrating a drive shaft of a fourth embodiment as viewed in an axial direction.
    • [FIG. 15] FIG. 15 is a diagram illustrating a drive shaft of a fifth embodiment as viewed in an axial direction.
    • [FIG. 16] FIG. 16 is a longitudinal sectional view illustrating a configuration of a rotary compressor according to a sixth embodiment.
    • [FIG. 17] FIG. 17 is a diagram illustrating a configuration of a drive shaft as viewed in an axial direction.
    DESCRIPTION OF EMBODIMENTS «First Embodiment»
  • As illustrated in FIG. 1, a rotary compressor (10) is provided in a refrigeration apparatus (1). The refrigeration apparatus (1) includes a refrigerant circuit (1a) filled with a refrigerant. The refrigerant circuit (1a) includes the rotary compressor (10), a radiator (3), a decompression mechanism (4), and an evaporator (5). The decompression mechanism (4) is, for example, an expansion valve. The refrigerant circuit (1a) performs a vapor compression refrigeration cycle.
  • The refrigeration apparatus (1) is an air conditioner. The air conditioner may be any of a cooling-only apparatus, a heating-only apparatus, or an air conditioner switchable between cooling and heating. In this case, the air conditioner has a switching mechanism (e.g., a four-way switching valve) configured to switch the direction of circulation of the refrigerant. The refrigeration apparatus (1) may be a water heater, a chiller unit, or a cooling apparatus configured to cool air in an internal space. The cooling apparatus cools the air in an internal space of a refrigerator, a freezer, a container, or the like.
  • As illustrated in FIG. 2, the rotary compressor (10) includes a casing (11), a drive mechanism (20), and a compression mechanism (50).
  • The casing (11) is configured as a vertically long cylindrical closed container. A suction pipe (16) passes through, and is fixed to, the barrel of the casing (11). An accumulator (not shown) is connected to the suction pipe (16). A discharge pipe (17) passes through, and is fixed to, an upper portion of the casing (11).
  • The casing (11) has an oil reservoir (18) at its bottom. The oil reservoir (18) stores oil. The oil is used to lubricate sliding portions of the compression mechanism (50) and a drive shaft (25).
    • <Drive Mechanism>
  • The drive mechanism (20) is housed in the casing (11). The drive mechanism (20) includes a motor (21) and the drive shaft (25). The motor (21) is disposed above the compression mechanism (50). The motor (21) includes a stator (22) and a rotor (23).
  • The stator (22) is fixed to the inner circumferential surface of the casing (11). The rotor (23) passes through the stator (22) in the up-and-down direction. The drive shaft (25) is fixed inside the axial center of the rotor (23). The drive shaft (25) is driven to rotate together with the rotor (23) when the motor (21) is energized.
  • The drive shaft (25) is arranged on the axis of the casing (11). An oil passage (30) is formed inside the drive shaft (25). A centrifugal oil supply pump (28) is provided at the lower end of the drive shaft (25). A lower portion of the oil supply pump (28) has an intake port (28a). The oil supply pump (28) conveys the oil stored in the oil reservoir (18). The conveyed oil is supplied to the sliding portions of the compression mechanism (50) and the drive shaft (25) through the oil passage (30) in the drive shaft (25).
  • The drive shaft (25) has a main shaft portion (26) and an eccentric portion (27). An upper portion of the main shaft portion (26) is fixed to the rotor (23) of the motor (21). The eccentric portion (27) has an axis decentered by a predetermined distance with respect to the axis of the main shaft portion (26).
  • Part of the main shaft portion (26) above the eccentric portion (27) is rotatably supported by a front head (52) described later. Part of the main shaft portion (26) below the eccentric portion (27) is rotatably supported by a rear head (53) described later.
    • <Compression Mechanism>
  • The compression mechanism (50) is housed in the casing (11). The compression mechanism (50) is disposed below the motor (21). The compression mechanism (50) includes a cylinder (51), the front head (52), the rear head (53), and a piston (54).
  • The cylinder (51) is formed as a flat and substantially annular member. The cylinder (51) has a circular compression chamber (55) at its center. The cylinder (51) has a suction passage (56) extending in a radial direction. The downstream end of the suction passage (56) communicates with the compression chamber (55). The suction pipe (16) is connected to the upstream end of the suction passage (56).
  • The front head (52) is disposed on an upper portion of the cylinder (51). The front head (52) covers the internal space of the cylinder (51) from above. The front head (52) rotatably supports the main shaft portion (26) of the drive shaft (25). The front head (52) has a discharge passage (not shown) passing therethrough in the axial direction.
  • The rear head (53) is disposed on a lower portion of the cylinder (51). The rear head (53) covers the internal space of the cylinder (51) from below. The rear head (53) rotatably supports the main shaft portion (26) of the drive shaft (25).
  • As illustrated also in FIG. 3, the piston (54) is housed in the cylinder (51). A blade (57) is integrated with the piston (54). The compression chamber (55) is defined by the cylinder (51) and the piston (54). The piston (54) has a perfectly circular annular shape. The eccentric portion (27) of the drive shaft (25) is fitted in the piston (54).
  • The interior of the compression chamber (55) is partitioned into a low-pressure chamber (55a) and a high-pressure chamber (55b) by the blade (57) (see FIG. 11). The blade (57) is supported by a pair of bushes (58), which allow oscillation of the blade (57).
  • The piston (54) rotates eccentrically in the cylinder (51) when the drive shaft (25) is driven to rotate. The refrigerant flowing through the suction pipe (16) is sucked into the low-pressure chamber (55a) through the suction passage (56) as the volume of the low-pressure chamber (55a) is gradually increased by the eccentric rotation of the piston (54).
  • Next, the low-pressure chamber (55a) is isolated from the suction passage (56), and the isolated space forms the high-pressure chamber (55b). The internal pressure of the high-pressure chamber (55b) increases as the volume of the high-pressure chamber (55b) gradually decreases. When the internal pressure of the high-pressure chamber (55b) exceeds a predetermined pressure, the refrigerant in the high-pressure chamber (55b) flows out of the compression mechanism (50) through a discharge passage (59). The high-pressure refrigerant flows upward through the internal space of the casing (11) and passes through a core cut (not shown) of the motor (21) or any other passage. The high-pressure refrigerant that has flowed upward of the motor (21) is transferred to the refrigerant circuit (1a) through the discharge pipe (17).
    • <Oil Passage>
  • Centrifugal force and gas load are applied to the drive shaft (25) as the compression mechanism (50) is driven and rotates, resulting in an increase in the shaft deflection of the drive shaft (25).
  • To address this, the inventors of this application have focused on the oil passage (30) that is a cause of lower rigidity of the drive shaft (25), and have studied how to increase the rigidity of the drive shaft (25) through improvement in the shape of the oil passage (30).
  • As illustrated in FIG. 2, the drive shaft (25) has the oil passage (30). The oil passage (30) includes an oil hole (31), a lower end hole (35), and lateral holes (36).
  • The lower end hole (35) is open at a lower end portion of the main shaft portion (26) of the drive shaft (25). The oil supply pump (28) is attached to the lower end hole (35). The oil hole (31) communicates with the lower end hole (35) and extends upward. The lateral holes (36) communicate with the oil hole (31) and extend in the horizontal direction. Each lateral hole (36) opens at a location that allows oil to be supplied to sliding portions of the compression mechanism (50) and the drive shaft (25).
  • In the example shown in FIG. 2, the lateral holes (36) are open to the sliding surfaces of the front head (52), the rear head (53), and the piston (54). A vent hole (37) is formed in a portion of the drive shaft (25) above the front head (52). The vent hole (37) discharges gas contained in the oil passing through the oil passage (30).
  • The oil flowing through the oil hole (31) is discharged to the outside of the drive shaft (25) through the lateral holes (36) by centrifugal force generated by the rotation of the drive shaft (25), and is supplied to the sliding portions of the compression mechanism (50) and the drive shaft (25).
  • As illustrated in FIG. 4, the axis of the main shaft portion (26) is referred to as the axis (C1), and the axis of the eccentric portion (27) is referred to as the axis (C2). As viewed in the axial direction of the drive shaft (25), a predetermined direction in a region surrounded by a phantom envelope (40) that envelops the oil hole (31) is referred to as a first direction (Y), and a direction orthogonal to the first direction (Y) is referred to as a second direction (X).
  • In the example shown in FIG. 4, as viewed in the axial direction of the drive shaft (25), the direction that connects the axis (C1) of the main shaft portion (26) and the axis (C2) of the eccentric portion (27) is referred to as the first direction (Y), and the direction orthogonal to the first direction (Y) is referred to as the second direction (X), as non-limiting configurations.
  • The oil passage (30) is formed as a long oil hole (31) extending along the first direction (Y) as viewed in the axial direction. Here, the length of the oil hole (31) in the second direction (X) is referred to as x, and the length of the oil hole (31) in the first direction (Y) is referred to as y. The long oil hole (31) can be represented as a locus of a circle having a diameter x that is moved continuously in the first direction (Y). Here, a curve that is a tangent to all the circles is referred to as an "envelope." In the example shown in FIG. 4, a phantom envelope (40) that envelops the oil hole (31) as viewed in the axial direction is indicated by the phantom line. The phantom envelope (40) is represented as a curve in the form of a long hole extending along the inner peripheral edge of the oil hole (31).
  • As viewed in the axial direction, the oil passage (30) has the length y in the first direction (Y) that is greater than the length x in the second direction (X) in a region surrounded by the phantom envelope (40) that envelops the oil hole (31). This can improve the rigidity of the drive shaft (25) and reduce the shaft deflection.
  • Specifically, if the oil passage has a circular shape having a diameter corresponding to the length of the first direction (Y), is greater in hole diameter than the intake port (28a), and is provided at a central portion of the drive shaft (25) to suck up oil by a centrifugal pumping action, this indicates that the drive shaft (25) has a relatively large hollow portion in its central portion (see the region surrounded by the phantom line in FIG. 5), which may reduce the rigidity of the drive shaft (25).
  • In contrast, by setting the length of the oil passage (30) in the second direction (X) to be shorter than the length in the first direction (Y), the area of the oil passage (30) can be made smaller than that of a circular oil passage provided at the central portion of the drive shaft (25), thereby improving the rigidity of the drive shaft (25) and reducing the shaft deflection.
  • By making the distance from the center of rotation of the drive shaft (25) to the inner wall surface of the oil passage (30) at a point farthest from the center of rotation in the radial direction equivalent to the radius of a circular oil passage, an equivalent centrifugal pumping action can be obtained (see FIG. 5).
  • Further, by forming the oil passage (30) such that the length in the first direction (Y) is greater than the length in the second direction (X) in a region surrounded by the phantom envelope (40), it is possible to make the rigidity of the drive shaft (25) in the second direction (X) higher than the rigidity in the first direction (Y).
  • The relationship between the shape of the oil hole (31) and the bending rigidity of the drive shaft (25) will be described below with reference to FIG. 6 and FIG. 7. In FIG. 6 and FIG. 7, only the main shaft portion (26) of the drive shaft (25) is shown, and the eccentric portion (27) is not shown. For ease of description, the oil hole (31) is described not in the form of a long hole extending in the first direction (Y) but in the form of a rectangle close to the long hole and extending in the first direction (Y).
  • As illustrated in FIG. 6, the diameter of the main shaft portion (26) is referred to as D. When load is applied to the main shaft portion (26) of the drive shaft (25) in the first direction (Y), the second moment of area Iy is calculated by the following formula (1). Iy = π ⋅ D 4 / 64 − x ⋅ y 3 / 12
  • On the other hand, as illustrated in FIG. 7, when load is applied to the main shaft portion (26) of the drive shaft (25) in the second direction (X), the second moment of area Ix is calculated by the following formula (2). Ix = π ⋅ D 4 / 64 − y ⋅ x 3 / 12
  • Here, since "x < y" is satisfied, the value Iy including "y3" decreases more significantly than the value Ix including "y". That is, "Ix > Iy" is satisfied, which indicates the bending rigidity of the drive shaft (25) in the second direction (X) is higher than the bending rigidity in the first direction (Y).
  • Next, the relationship between the rotational angle of the drive shaft (25) and the load applied to the drive shaft (25) will be described with reference to the graphs of FIGS. 8 to 10. As illustrated in FIG. 3, the position at which the eccentric portion (27) of the drive shaft (25) is directed upward in FIG. 3 is referred to as the top dead center 0°.
  • FIG. 8 is a graph showing the relationship between an angle from the top dead center and the magnitude of force applied to the drive shaft (25). In the case of FIG. 8, a maximum gas load during the rotational driving of the compression mechanism (50) is applied to the drive shaft (25) at a position rotated 227° from the top dead center 0°.
  • FIG. 9 is a graph showing the relationship between an angle from the top dead center and the direction of force applied to the drive shaft (25). As shown in FIG. 9, the direction of the gas load applied to the drive shaft (25) is 119.18° (≈ 119°) at the position of 227°, which is an angle at which the maximum gas load is applied during the rotational driving of the compression mechanism (50).
  • FIG. 10 is a graph showing the relationship between an angle from the top dead center and the direction of gas load applied to the drive shaft (25) when the direction of eccentricity of the eccentric portion (27) is taken as a reference 0°. As shown in FIG. 10, when the direction of eccentricity of the eccentric portion (27) is taken as the reference 0°, the direction of the gas load applied to the drive shaft (25) is -107.82° (≈ -108°) at the position of 227°, which a rotational angle at which the maximum gas load is applied during the rotational driving of the compression mechanism (50).
  • FIG. 11 is a diagram illustrating the angle at which the maximum gas load is applied to the drive shaft (25). In FIG. 11, the maximum gas load during the rotational driving of the compression mechanism (50) is applied to the drive shaft (25) at the position rotated 227° from the top dead center 0°, in a direction rotated 108° counterclockwise from the first direction (Y) connecting the axis (C1) of the main shaft portion (26) and the axis (C2) of the eccentric portion (27). In FIG. 11, the load direction is indicated by the white arrow.
  • Here, the direction of the maximum gas load during the rotational driving of the compression mechanism (50) varies in the range of 80° to 110°, for example, depending on compression conditions or the like. The second direction (X) is the direction orthogonal to the first direction (Y), that is, a direction rotated 90° with respect to the first direction (Y), and is thus included in the range of directions of the maximum gas load from 80° to 110°.
  • As described above, the rigidity of the drive shaft (25) in the second direction (X) is higher than the rigidity in the first direction (Y). Thus, the shaft deflection of the drive shaft (25) can be reduced even if the maximum gas load during the rotational driving of the compression mechanism (50) is applied to the drive shaft (25) in the second direction (X).
  • To further improve the rigidity of the drive shaft (25) against the maximum gas load during the rotational driving of the compression mechanism (50), the shape of the oil passage (30) may be determined so that the direction of the maximum gas load (108°) coincides with the angle of the second direction (X).
  • It is preferable that the length y of the oil hole (31) in the first direction (Y) is determined so that both ends of the phantom envelope (40) in the first direction (Y) are located radially outward of the intake port (28a) of the oil supply pump (28), as viewed in the axial direction. This configuration enables smooth supply of oil through a centrifugal pump using centrifugal force generated by the rotation of the drive shaft (25).
    • -Advantages of First Embodiment-
  • According to a feature of this embodiment, the rigidity of the drive shaft (25) can be increased by forming the oil passage (30) such that the length in the first direction (Y) is greater than the length in the second direction (X) in the region surrounded by the phantom envelope (40).
  • Thus, even when the centrifugal force is applied to the drive shaft (25) by the eccentric weights of the eccentric portion (27) and the piston (54) during rotation of the drive shaft (25), the shaft deflection of the drive shaft (25) can be reduced.
  • Further, by setting the distance from the center of rotation of the drive shaft (25) to the inner wall surface of the oil passage (30) at a point farthest from the center of rotation in the radial direction to be equivalent to the radius of a circular oil passage, an equivalent centrifugal pumping action can be obtained.
  • Reduction of the shaft deflection of such a drive shaft (25) makes it possible to reduce noise generated by whirling of the drive shaft (25).
  • According to a feature of this embodiment, the rigidity of the drive shaft (25) in the second direction (X) is higher than the rigidity in the first direction (Y). Thus, the shaft deflection of the drive shaft (25) can be reduced even if the maximum gas load during the rotational driving of the compression mechanism (50) is applied to the drive shaft (25) in the second direction (X).
  • According to a feature of this embodiment, by forming the oil passage (30) as the long oil hole (31) extending along the first direction (Y) as viewed in the axial direction, the rigidity of the drive shaft (25) in the second direction (X) can be higher than the rigidity in the first direction (Y).
  • According to a feature of this embodiment, the oil passage (30) having a shape in which the length in the first direction (Y) is greater than the length in the second direction (X) in the region surrounded by the phantom envelope (40) is applicable to a rotary compressor in which the compression mechanism (50) is arranged below the motor (21).
  • According to a feature of this embodiment, it is possible to provide a refrigeration apparatus including the rotary compressor (10) and the refrigerant circuit (1a).
    • «Second Embodiment»
  • In the following description, the same reference characters designate the same components as those of the first embodiment, and the description is focused only on the difference.
  • As illustrated in FIG. 12, the oil hole (31) of the oil passage (30) is formed as a rectangular hole extending along the first direction (Y) as viewed in the axial direction. In the example shown in FIG. 12, a phantom envelope (40) that envelops the oil hole (31) as viewed in the axial direction is indicated by the phantom line. The phantom envelope (40) is represented as lines in the form of a rectangle extending along the inner peripheral edge of the oil hole (31).
  • As viewed in the axial direction, the oil passage (30) has the length y in the first direction (Y) that is greater than the length x in the second direction (X) in a region surrounded by the phantom envelope (40) that envelops the oil hole (31).
    • -Advantages of Second Embodiment-
  • According to a feature of this embodiment, the rigidity of the drive shaft (25) in the second direction (X) can be higher than the rigidity in the first direction (Y).
    • «Third Embodiment»
  • As illustrated in FIG. 13, the oil passage (30) is formed by a plurality of oil holes (31) arranged along the first direction (Y) as viewed in the axial direction. All the multiple oil holes (31) are formed to have the same inside diameter. In the example shown in FIG. 13, four oil holes (31) are arranged along the first direction (Y), which is merely an example and is not limited thereto. In the example shown in FIG. 13, a phantom envelope (40) that envelops the plurality of oil holes (31) as viewed in the axial direction is indicated by the phantom line. The phantom envelope (40) is represented as a curve in the form of a long hole extending along the first direction (Y).
  • As viewed in the axial direction, the oil passage (30) has the length y in the first direction (Y) that is greater than the length x in the second direction (X) in a region surrounded by the phantom envelope (40) that envelops the plurality of oil holes (31).
  • In this embodiment, the multiple oil holes (31) are arranged symmetrically with respect to the axis (C1) of the main shaft portion (26), but are not limited thereto. The oil holes (31) may be arranged asymmetrically.
  • It is preferable that positions of the oil holes (31) in the first direction (Y) are determined so that both ends of the phantom envelope (40) in the first direction (Y) are located radially outward of the intake port (28a) of the oil supply pump (28), as viewed in the axial direction. This configuration enables smooth supply of oil through a centrifugal pump using centrifugal force generated by the rotation of the drive shaft (25).
  • Two oil holes (31) located between the oil holes (31) located at both ends in the first direction (Y) are used to discharge gas contained in the oil through the vent hole (37).
    • -Advantages of Third Embodiment-
  • According to a feature of this embodiment, by forming the oil passage (30) as a plurality of oil holes (31) arranged along the first direction (Y), the rigidity of the drive shaft (25) in the second direction (X) can be higher than the rigidity in the first direction (Y).
    • «Fourth Embodiment»
  • As illustrated in FIG. 14, the oil passage (30) is formed by a plurality of oil holes (31) arranged along the first direction (Y) as viewed in the axial direction. The plurality of oil holes (31) includes holes having different inside diameters. In the example shown in FIG. 14, three oil holes (31) are spaced apart from one another in the first direction (Y), which is merely an example and is not limited thereto. Among the three oil holes (31), the oil hole (31) located in the middle in the first direction (Y) has a larger inside diameter than the oil holes (31) located at both ends in the first direction (Y).
  • In the example shown in FIG. 14, a phantom envelope (40) that envelops the plurality of oil holes (31) as viewed in the axial direction is indicated by the phantom line. The phantom envelope (40) is represented as a curve defining a shape in which the length x in the second direction (X) is greatest at the middle in the first direction (Y) and gradually decreases toward both ends in the second direction (X).
  • As viewed in the axial direction, the oil passage (30) has the length y in the first direction (Y) that is greater than the length x in the second direction (X) in a region surrounded by the phantom envelope (40) that envelops the plurality of oil holes (31). In this description, the length x at the middle in the second direction (X), which is the greatest length x in the second direction (X), is compared to the length y in the first direction (Y).
  • The oil hole (31) located between the oil holes (31) located at both ends in the first direction (Y) is used to discharge gas contained in the oil through the vent hole (37).
    • -Advantages of Fourth Embodiment-
  • According to a feature of this embodiment, by forming the oil passage (30) as a plurality of oil holes (31) arranged along the first direction (Y), the rigidity of the drive shaft (25) in the second direction (X) can be higher than the rigidity in the first direction (Y).
    • «Fifth Embodiment»
  • As illustrated in FIG. 15, the oil passage (30) is formed by a plurality of oil holes (31) arranged along the first direction (Y) as viewed in the axial direction. All the multiple oil holes (31) are formed to have the same inside diameter. In the oil passage (30), the oil holes (31) are arranged so that the oil holes (31) adjacent to each other partially overlap each other as viewed in the axial direction.
  • In the example shown in FIG. 15, a phantom envelope (40) that envelops the plurality of oil holes (31) as viewed in the axial direction is indicated by the phantom line. The phantom envelope (40) is represented as a curve in the form of a long hole extending along the first direction (Y).
  • As viewed in the axial direction, the oil passage (30) has the length y in the first direction (Y) that is greater than the length x in the second direction (X) in a region surrounded by the phantom envelope (40) that envelops the plurality of oil holes (31).
    • -Advantages of Fifth Embodiment-
  • According to a feature of this embodiment, assuming that the length in the first direction (Y) of the region surrounded by the phantom envelope (40) is constant, the number of oil holes (31) in the region surrounded by the phantom envelope (40) is greater when adjacent oil holes (31) partially overlap with each other than when adjacent oil holes (31) are spaced apart from each other. Thus, machining the oil passage (30) into a long-hole shape becomes easier.
    • «Sixth Embodiment»
  • As illustrated in FIG. 16, the rotary compressor (10) includes a casing (11), a drive mechanism (20), and a compression mechanism (50).
  • The drive mechanism (20) includes a motor (21) and a drive shaft (25). The drive shaft (25) has a main shaft portion (26) and two eccentric portions (27). The eccentric portions (27) each have an axis decentered by a predetermined distance with respect to the axis of the main shaft portion (26). The two eccentric portions (27) are eccentric in directions that differ from each other by 180° (see also FIG. 17).
  • The compression mechanism (50) includes two cylinders (51), a front head (52), a rear head (53), two pistons (54), and a middle plate (60). The middle plate (60) is sandwiched between the two cylinders (51).
  • As illustrated in FIG. 17, the axis of the main shaft portion (26) is referred to as the axis (C1), and the axes of the two eccentric portions (27) are referred to as the axes (C2). As viewed in the axial direction of the drive shaft (25), a predetermined direction in a region surrounded by a phantom envelope (40) that envelops the oil hole (31) is referred to as a first direction (Y), and a direction orthogonal to the first direction (Y) is referred to as a second direction (X).
  • In the example shown in FIG. 17, as viewed in the axial direction of the drive shaft (25), the direction that connects the axis (C1) of the main shaft portion (26) and the axis (C2) of each eccentric portion (27) is referred to as the first direction (Y), and the direction orthogonal to the first direction (Y) is referred to as the second direction (X), as non-limiting configurations.
  • The oil passage (30) is formed as a long oil hole (31) extending along the first direction (Y) as viewed in the axial direction. In the example shown in FIG. 17, the phantom envelope (40) that envelops the oil hole (31) as viewed in the axial direction is indicated by the phantom line. The phantom envelope (40) is represented as a curve in the form of a long hole extending along the inner peripheral edge of the oil hole (31).
  • As viewed in the axial direction, the oil passage (30) has the length y in the first direction (Y) that is greater than the length x in the second direction (X) in a region surrounded by the phantom envelope (40) that envelops the oil hole (31).
  • The oil passage (30) may be formed by a plurality of oil holes (31) arranged along the first direction (Y) as viewed in the axial direction, similarly to the third embodiment described above. Alternatively, the oil passage (30) may be formed by a plurality of oil holes (31) arranged so that the oil holes (31) adjacent to each other partially overlap each other, as viewed in the axial direction, similarly to the fifth embodiment described above.
    • -Advantages of Sixth Embodiment-
  • According to a feature of this embodiment, the rigidity of the drive shaft (25) in the second direction (X) can be higher than the rigidity in the first direction (Y).
    • «Other Embodiments»
  • The above-described embodiments may be modified as follows.
  • In this embodiment, the oil hole (31) of the oil passage (30) is formed as a long hole extending along the first direction (Y) as viewed in the axial direction, but is not limited thereto. For example, the oil hole (31) may be formed as an elliptical hole extending along the first direction (Y) as viewed in the axial direction.
  • In this embodiment, the oil supply pump (28) is attached to the lower end of the drive shaft (25) so that oil can be sucked up through the oil supply pump (28), but is not limited thereto. For example, the drive shaft (25) may be extended to a position where its lower end is immersed in oil in the oil reservoir (18), and the lower end hole (35) of the oil passage (30), which is open to the lower end of the drive shaft (25), may be covered with an end plate member (not shown) having a central inlet hole. Thus, oil can be sucked up through the inlet hole of the end plate member into the oil passage (30) of the drive shaft (25).
  • The plurality of oil holes (31) may be used according to their respective purposes. For example, one of the oil holes (31) may be used as a passage for supplying oil to the sliding portions between the drive shaft (25) and the front and rear heads (52) and (53), while another oil hole (31) may be used as a passage for supplying oil to the cylinder (51).
  • While the embodiments have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the claims. The elements according to the embodiments, the variations thereof, and the other embodiments may be combined and replaced with each other. In addition, the expressions of "first," "second," "third," . . . , in the specification and claims are used to distinguish the terms to which these expressions are given, and do not limit the number and order of the terms.
    • INDUSTRIAL APPLICABILITY
  • As can be seen from the foregoing description, the present disclosure is useful for a rotary compressor and a refrigeration apparatus.
    • DESCRIPTION OF REFERENCE CHARACTERS
    • 1
    Refrigeration Apparatus
    1a
    Refrigerant Circuit
    10
    Rotary Compressor
    21
    Motor
    25
    Drive Shaft
    26
    Main Shaft Portion
    27
    Eccentric Portion
    30
    Oil Passage
    31
    Oil Hole
    40
    Phantom Envelope
    50
    Compression Mechanism
    C1
    Axis
    C2
    Axis
    X
    Second Direction
    Y
    First Direction

Claims (7)

  1. A rotary compressor comprising: a compression mechanism (50); and a drive shaft (25) configured to rotationally drive the compression mechanism (50),
    the drive shaft (25) including a main shaft portion (26) and an eccentric portion (27), the eccentric portion (27) being eccentric with respect to an axis (C1) of the main shaft portion (26) by a predetermined distance,
    the drive shaft (25) having an oil passage (30) including one or more oil holes (31) extending in an axial direction,
    as viewed in the axial direction of the drive shaft (25), a predetermined direction in a region surrounded by a phantom envelope (40) that envelops the one or more oil holes (31) being referred to as a first direction (Y), a direction orthogonal to the first direction (Y) being referred to as a second direction (X),
    as viewed in the axial direction, the oil passage (30) has a length in the first direction (Y) that is greater than a length in the second direction (X) in the region surrounded by the phantom envelope (40).
  2. The rotary compressor of claim 1, wherein
    the first direction (Y) is a direction that connects the axis (C1) of the main shaft portion (26) and an axis (C2) of the eccentric portion (27), as viewed in the axial direction of the drive shaft (25).
  3. The rotary compressor of claim 1 or 2, wherein
    the oil passage (30) is formed as a long oil hole (31) extending along the first direction (Y) as viewed in the axial direction.
  4. The rotary compressor of claim 1 or 2, wherein
    the oil passage (30) is formed by the plurality of oil holes (31) arranged along the first direction (Y) as viewed in the axial direction.
  5. The rotary compressor of claim 4, wherein
    in the oil passage (30), the plurality of oil holes (31) is arranged so that the oil holes (31) adjacent to each other partially overlap each other as viewed in the axial direction.
  6. The rotary compressor of any one of claims 1 to 5, further comprising:
    a motor (21) configured to rotate the drive shaft (25), wherein
    the compression mechanism (50) is disposed below the motor (21).
  7. A refrigeration apparatus, comprising: the rotary compressor (10) of any one of claims 1 to 6; and
    a refrigerant circuit (1a) through which a refrigerant compressed by the rotary compressor (10) flows.
EP24845226.0A 2023-07-27 2024-06-10 Rotary compressor and refrigeration apparatus Pending EP4729783A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2023122574 2023-07-27
PCT/JP2024/021094 WO2025022844A1 (en) 2023-07-27 2024-06-10 Rotary compressor and refrigeration apparatus

Publications (1)

Publication Number Publication Date
EP4729783A1 true EP4729783A1 (en) 2026-04-22

Family

ID=94374282

Family Applications (2)

Application Number Title Priority Date Filing Date
EP24845226.0A Pending EP4729783A1 (en) 2023-07-27 2024-06-10 Rotary compressor and refrigeration apparatus
EP24845303.7A Pending EP4729784A1 (en) 2023-07-27 2024-06-26 Rotary compressor and refrigeration apparatus

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP24845303.7A Pending EP4729784A1 (en) 2023-07-27 2024-06-26 Rotary compressor and refrigeration apparatus

Country Status (4)

Country Link
EP (2) EP4729783A1 (en)
JP (3) JP7695595B2 (en)
CN (2) CN121336047A (en)
WO (2) WO2025022844A1 (en)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50115806U (en) * 1974-03-05 1975-09-20
JPS55100714U (en) * 1979-01-10 1980-07-14
JPH01149586U (en) * 1988-04-07 1989-10-17
JPH089434Y2 (en) * 1990-01-29 1996-03-21 ダイキン工業株式会社 Hermetic compressor
JPH05312172A (en) * 1992-05-12 1993-11-22 Daikin Ind Ltd Rolling piston compressor
JP3635732B2 (en) * 1995-09-13 2005-04-06 松下電器産業株式会社 Scroll compressor
JP2008208752A (en) * 2007-02-26 2008-09-11 Daikin Ind Ltd Compressor
JP2015197044A (en) * 2014-03-31 2015-11-09 ダイキン工業株式会社 Rotary compressor
JP6036980B2 (en) * 2014-12-12 2016-11-30 ダイキン工業株式会社 Compressor
JP2017106423A (en) * 2015-12-11 2017-06-15 ダイキン工業株式会社 Compressor
CN113474560B (en) 2019-02-13 2022-11-29 三菱电机株式会社 Compressor and air conditioner
JP2022072807A (en) 2020-10-30 2022-05-17 ダイキン工業株式会社 Compressor, method of manufacturing compressor, and air conditioner

Also Published As

Publication number Publication date
JP2025018942A (en) 2025-02-06
EP4729784A1 (en) 2026-04-22
JP2025018952A (en) 2025-02-06
CN121263605A (en) 2026-01-02
JP7695595B2 (en) 2025-06-19
JP2025071307A (en) 2025-05-02
WO2025022844A1 (en) 2025-01-30
WO2025022921A1 (en) 2025-01-30
CN121336047A (en) 2026-01-13

Similar Documents

Publication Publication Date Title
US7462021B2 (en) Rotary compressor, and car air conditioner and heat pump type water heater using the compressor
JP6787480B2 (en) Rotary compressor
US12565891B2 (en) Compressor unit and refrigeration apparatus with reduced vibrations
KR101971819B1 (en) Scroll compressor
US12421967B2 (en) Rotary compressor and refrigeration device
CN103582762B (en) Hermetic type compressor and refrigerating circulatory device
US11906060B2 (en) Rotary compressor with backflow suppresion mechanism for an introduction path
JP2008240666A (en) Rotary compressor and heat pump system
EP3988792B1 (en) Hermetic compressor and refrigeration cycle device
EP3636929B1 (en) Rotary compressor
US10968911B2 (en) Oscillating piston-type compressor
JP7695595B2 (en) Rotary compressor and refrigeration device
KR102861985B1 (en) Scroll compressor
EP4459128A1 (en) Rotary compressor and refrigeration apparatus
CN114555948B (en) Compressors and Refrigeration Cycle Units
JP6841272B2 (en) Rotary compressor
US20240230175A1 (en) Compressor unit and refrigeration apparatus
EP4474651A1 (en) Rotary compressor and refrigeration apparatus
EP4461962A1 (en) Rotary compressor and refrigeration device
WO2026069827A1 (en) Refrigerant compressor, refrigeration device, and air-conditioning system
JP6769078B2 (en) Rotary compressor
KR20240111230A (en) Scroll compressor
EP4707601A1 (en) Rotary compressor and refrigeration device
JP5003085B2 (en) Rotary fluid machine
CN111065824A (en) Rotary compressor

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20260116

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC ME MK MT NL NO PL PT RO RS SE SI SK SM TR