US20190017506A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
US20190017506A1
US20190017506A1 US16/065,958 US201616065958A US2019017506A1 US 20190017506 A1 US20190017506 A1 US 20190017506A1 US 201616065958 A US201616065958 A US 201616065958A US 2019017506 A1 US2019017506 A1 US 2019017506A1
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United States
Prior art keywords
housing
key
scroll
facing portion
ring
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.)
Abandoned
Application number
US16/065,958
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English (en)
Inventor
Masahiro Yamada
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
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Publication date
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Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YAMADA, MASAHIRO
Publication of US20190017506A1 publication Critical patent/US20190017506A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—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
    • F04C18/0207—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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/04—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow radial displacement, e.g. Oldham couplings

Definitions

  • the present disclosure relates to a scroll compressor provided with a compression mechanism having a fixed scroll and an orbiting scroll, and in particular, to a structure of allowing the compression mechanism to hold an Oldham ring that is a mechanism preventing the orbiting scroll from rotating on its axis.
  • an Oldham ring ( 100 ) is typically used to allow revolution of an orbiting scroll (not illustrated) while substantially preventing rotation of the orbiting scroll on its axis, as illustrated in FIG. 17 that is a plan view of a housing and the Oldham ring, FIG. 18 that is a cross-sectional view taken along line XVIII-XVIII of FIG. 17 , FIG. 19 that is a plan view of the Oldham ring, and FIG. 20 that is a cross-sectional view taken along line XX-XX of FIG. 19 .
  • the Oldham ring ( 100 ) is comprised of a ring portion ( 101 ) and keys ( 102 , 103 ) which are integrally formed together.
  • the Oldham ring ( 100 ) includes a pair of keys ( 102 ) and another pair of keys ( 103 ), the keys ( 102 ) being disposed on a surface of the ring portion ( 101 ) closer to a housing ( 110 ), the keys ( 103 ) being disposed on another surface of the ring portion ( 101 ) closer to the orbiting scroll.
  • the pair of keys ( 102 ) protrudes from the surface of the ring portion ( 101 ) closer to the housing ( 110 ) in a direction perpendicular to the surface.
  • the other pair of keys ( 103 ) protrude from the surface of the ring portion ( 101 ) closer to the orbiting scroll in a direction perpendicular to the surface.
  • the housing ( 110 ) is provided with an annular opening ( 111 .) movably housing the ring portion ( 101 ) and a key groove ( 112 ) engaged with the keys ( 102 ).
  • Patent Document 1 discloses, as a modification of the above structure, a structure in which the keys ( 102 , 103 ) are disposed so as to protrude radially outwardly from the ring portion ( 101 ), as illustrated in FIGS. 21 to 24 .
  • Patent Document 2 discloses, as illustrated in FIGS. 25 to 28 , a structure in which one pair of keys ( 102 ) of the pair of keys ( 102 ) and the pair of keys ( 103 ) of the Oldham ring ( 100 ) are formed to protrude radially inwardly from the ring portion ( 101 ), and not to protrude in the direction perpendicular to the surface.
  • Patent Document 1 Japanese Unexamined Patent Publication No. 2010-185462
  • Patent Document 2 Japanese Unexamined Patent Publication No. S63-138181
  • the typical configuration of the Oldham ring ( 100 ) shown in FIGS. 17 to 20 has a small sliding area between the key ( 102 ) and the key groove ( 112 ), and thus, a contact pressure of the key sliding surface is increased, resulting in insufficient strength of the keys ( 102 ) of the Oldham ring ( 100 ).
  • the outer periphery of the housing ( 110 ) may have to be provided with a notch ( 115 ), resulting in decreased strength of the housing ( 110 ).
  • the keys ( 102 , 103 ) are formed in the radially outside of the ring portion ( 101 ), and thus, a moment applied to the keys ( 102 , 103 ) is increased, resulting in decreased strength of the Oldham ring ( 100 ).
  • the key groove ( 112 ) of the housing ( 110 ) is formed on an orbiting scroll facing surface ( 120 ) on which the orbiting scroll (not illustrated) faces the surface of the housing ( 110 ), and thus, the effective area of the orbiting scroll facing surface ( 120 ) is decreased, resulting in increased contact pressure.
  • the sealing ring may hinder the formation of the key groove ( 112 ).
  • a first aspect of the present disclosure is directed to a scroll compressor including: a housing ( 23 ) into which a drive shaft ( 40 ) is inserted: an Oldham ring ( 50 ) configured to be slidable on the housing ( 23 ) by a first key mechanism ( 51 ) in a first direction perpendicular to an axial center of drive shaft ( 40 ); a fixed scroll ( 21 ) fixed to the housing ( 23 ); and an orbiting scroll ( 22 ) meshing with the fixed scroll ( 21 ) and configured to be slidable on the Oldham ring ( 50 ) by a second key mechanism ( 52 ) in a second direction perpendicular to the axial center of drive shaft ( 40 ), the first key mechanism ( 51 ) including a first key ( 54 ) provided to the Oldham ring ( 50 ) and a first key groove ( 61 ) formed in the housing ( 23 ).
  • the housing ( 23 ) includes a flange ( 23 a ) to which the fixed scroll ( 21 ) is fixed and which includes a facing portion ( 71 ) having a predetermined thickness and having an orbiting scroll facing surface ( 70 ) facing the orbiting scroll ( 22 ), and an annular opening ( 72 ) formed around the orbiting scroll facing surface ( 70 ) and movably housing the ring portion ( 53 ), and the first key groove ( 61 ) is formed in a position adjacent to a back surface of the facing portion ( 71 ) opposite to the orbiting scroll facing surface ( 70 ) so as to extend radially inwardly from the annular opening ( 72 ).
  • the orbiting scroll facing surface ( 70 ) facing the orbiting scroll ( 22 ) may be in contact
  • the first key ( 64 ) protrudes from the ring portion ( 53 ) of the Oldham ring ( 50 ) toward the housing ( 23 ) and further protrudes in the radially inward direction of the ring portion ( 53 ). This can sufficiently increase the area of the sliding surface between the first key ( 54 ) and the first key groove ( 61 ) to reduce a contact pressure of the key sliding surface.
  • the first key ( 54 ) protrudes in the radially inward direction of the Oldham ring ( 50 ), the outer periphery of the housing ( 23 ) does not have to be notched, and the moment of the first key ( 54 ) can be reduced.
  • the first key groove ( 61 ) is formed in the position adjacent to the back side of the orbiting scroll facing surface ( 70 ) (in the position adjacent to the back surface of the facing portion ( 71 )), and thus, the first key groove ( 61 ) does not hinder the formation of the sealing ring.
  • a second aspect of the present disclosure is an embodiment of the first aspect.
  • the first key ( 54 ) includes a pair of first keys ( 54 ) opposed to each other by 180° on the Oldham ring ( 50 ), and an interval (A) between the pair of the first keys ( 54 ) is smaller than an outer diameter (B) of the facing portion ( 71 ) of the housing ( 23 ), and a thickness (C) of the ring portion ( 53 ) is larger than a thickness (D) of the facing portion ( 71 ) of the housing ( 23 ).
  • the second aspect satisfies the above dimension relationship, making it possible to easily attach the Oldham ring ( 50 ) to the housing ( 23 ) along an oblique direction, as illustrated in FIGS. 10 and 11 .
  • a third aspect of the present disclosure is an embodiment of the first or second aspect of the present disclosure.
  • the back surface of the facing portion ( 71 ) is a tilted surface ( 71 a ) such that a thickness of the facing portion ( 71 ) increases toward an inner periphery of the facing portion ( 71 ).
  • the back surface of the facing portion ( 71 ) is the tilted surface ( 71 a ), and thus, when the Oldham ring ( 50 ) is attached to the housing ( 23 ), the first key ( 54 ) can be easily inserted into the first key groove ( 61 ).
  • a fourth aspect of the present disclosure is an embodiment of the first, second, or third aspect of the present disclosure.
  • the first key groove ( 61 ) is a groove opened on a hack surface of the flange ( 23 a ) of the housing ( 23 ).
  • the first key ( 54 ) engages with the first key groove ( 61 ) opened on the back surface of the flange ( 23 a ) of the housing ( 23 ), allowing the Oldham ring ( 50 ) to operate.
  • a fifth aspect of the present disclosure is an embodiment of the first, second, or third aspect of the present disclosure.
  • the first key groove ( 61 ) is a groove opened on an outer peripheral surface of the flange ( 23 a ) of the housing ( 23 ).
  • the first key ( 54 ) engages with the first key groove ( 61 ) opened on the outer peripheral surface of the flange ( 23 a ) of the housing ( 23 ), allowing the Oldham ring ( 50 ) to operate.
  • a sixth aspect of the present disclosure is an embodiment of the first, second, or third. aspect of the present disclosure.
  • the facing portion ( 71 ) is configured as a separate member different from the housing ( 23 ) and fixed to a main body of the housing ( 23 ).
  • the first key groove ( 61 ) is formed by fixing the facing portion ( 71 ) configured as a separate member to the main body of the housing ( 23 ), and the first key ( 54 ) engages with the first key groove 61 ), allowing the Oldham ring ( 50 ) to operate.
  • the first key ( 64 ) protrudes from the ring portion ( 53 ) of the Oldham ring ( 50 ) toward the housing ( 23 ) and further protrudes in the radially inward direction of the ring portion ( 53 ).
  • This can sufficiently increase the area of the sliding surface between the first key ( 54 ) and the first key groove ( 61 ), and reduce a contact pressure of the key sliding surface contributing to preventing insufficient strength of the first key ( 54 ) of the Oldham ring ( 50 ).
  • the first key ( 54 ) protrudes in the direction radially inward of the Oldham ring ( 50 ), and the outer periphery of the housing ( 23 ) does not have to be notched.
  • the first key groove ( 61 ) is formed in the position adjacent to the back side of the orbiting scroll facing surface ( 70 ) (in the position adjacent to the back surface of the facing portion ( 71 )), the first key groove ( 61 ) does not hinder the formation of the sealing ring, and it is possible to use the seal ring ( 50 ) in a configuration in which the first key ( 54 ) and the first key groove ( 61 ) engage with each other.
  • the interval (A) between the pair of the first keys ( 54 ) is smaller than the outer diameter (B) of the facing portion ( 71 ) of the housing ( 23 ), and the thickness (C) of the ring portion ( 53 ) is larger than the thickness (D) of the facing portion ( 71 ) of the housing ( 23 ).
  • the Oldham ring ( 50 ) can be easily attached to the housing ( 23 ) along an oblique direction. Accordingly, the Oldham ring ( 50 ) does not have to be made large, making it possible to reduce the size of the mechanism.
  • the back surface of the facing portion ( 71 ) is the tilted surface ( 71 a ), and thus, when the Oldham ring ( 50 ) is attached to the housing ( 23 ), the first key ( 54 ) can be easily inserted into the first key groove ( 61 ), improving ease of attachment.
  • the first key groove ( 61 ) is a groove opened on the back surface of the flange ( 23 a ) of the housing ( 23 ), easily forming the first key groove ( 61 ).
  • the first key groove ( 61 ) which is a groove opened on the outer peripheral surface of the flange ( 23 a ) of the housing ( 23 ), can be easily formed.
  • the first key groove ( 61 ) can be easily formed by fixing the facing portion ( 71 ) configured as a separate member to the main body of the housing ( 23 ).
  • FIG. 1 is a vertical cross-sectional view of a scroll compressor according to an embodiment of the present disclosure.
  • FIG. 2 is a plan view illustrating a state in which an Oldham ring is being attached to a housing.
  • FIG. 3 is a cross-sectional view taken along line III-III FIG. 2 .
  • FIG. 4 is a plan view of the Oldham ring.
  • FIG. 5 is a cross-sectional view taken along line V-V of FIG. 4 .
  • FIG. 6 is a plan view illustrating a state in which the Oldham ring is being attached to the housing having a body whose back surface side is opened, and provided with a first key groove.
  • FIG. 7 is a cross-sectional view taken along line VII-VII of FIG. 6 .
  • FIG. 8 illustrates a relationship between the dimension of the housing and the dimension of the Oldham ring.
  • FIG. 9 illustrates a portion of FIG. 8 on an enlarged scale.
  • FIG. 10 is a plan view illustrating a first state in which the Oldham ring is being attached to the housing.
  • FIG. 11 is a plan view illustrating a second state in which the Oldham ring is being attached to the housing.
  • FIG. 12 is a partially enlarged cross-sectional view of a housing according to a first variation.
  • FIG. 13 is a partially enlarged cross-sectional view of a housing according to a second variation.
  • FIG. 14 is a plan view of a housing and an Oldham ring according to a third variation.
  • FIG. 15 is a cross-sectional view taken along line XV-XV of FIG. 14 .
  • FIG. 16 is a cross-sectional view of a main part of a compressor according to another embodiment.
  • FIG. 17 is a plan view illustrating a state in which an Oldham ring is being attached to a housing according to a first conventional example.
  • FIG. 18 is a cross-sectional view taken along line XVIII-XVIII of FIG. 17 .
  • FIG. 19 is a plan view of the Oldham ring of the first conventional example.
  • FIG. 20 is a cross-sectional view taken along line XX-XX of FIG. 19 .
  • FIG. 21 is a plan view illustrating a state in which an Oldham ring is being attached to a housing according to a second conventional example.
  • FIG. 22 is a cross-sectional view taken along line XXII-XXII of FIG. 21 .
  • FIG. 23 is a plan view of the Oldham ring of the second conventional example.
  • FIG. 24 is a cross-sectional view taken along line XXIV-XXIV of FIG. 23 .
  • FIG. 25 is a plan view illustrating a state in which an Oldham ring is being attached to a housing according to a third conventional example.
  • FIG. 26 is a cross-sectional view taken along line XXVI-XXVI of FIG. 25 .
  • FIG. 27 is a plan view of the Oldham ring of the third conventional example.
  • FIG. 28 is a cross-sectional view taken alone line XXVIII-XXVIII of 27 .
  • a scroll compressor is provided to, e.g., a refrigerant circuit of an air conditioner performing a vapor compression refrigeration cycle, and compresses a low-pressure refrigerant that has been sucked from an evaporator to discharge it into a condenser.
  • the scroll compressor ( 1 ) is a so-called hermetic compressor.
  • This scroll compressor ( 1 ) includes a casing ( 10 ) that is a hermetically-sealed container with a vertically oriented cylindrical shape.
  • the casing ( 10 ) includes a body ( 11 ) with a vertically oriented cylindrical shape, an upper end plate ( 12 ) fixed to the upper end of the body ( 11 ), and a lower end plate ( 13 ) fixed to the lower end of the body ( 11 ).
  • This casing ( 10 ) houses a compression mechanism ( 20 ) compressing a refrigerant, and an electric motor ( 45 ) driving the compression mechanism ( 20 ).
  • the electric motor ( 45 ) is disposed below the compression mechanism ( 20 ), and is coupled to the compression mechanism ( 20 ) through a drive shaft ( 40 ) that is a rotational shaft.
  • the electric motor ( 45 ) is implemented as a brushless DC motor controlled by an inverter to adjust a rotational speed to be variable.
  • a discharge pipe ( 5 ) passes through and is attached to the upper end plate ( 12 ) that is a top of the casing ( 10 ).
  • This discharge pipe ( 15 ) has its terminal end (the lower end in the figure) connected to the compression mechanism ( 20 ).
  • a suction pipe ( 14 ) passes through and is attached to the body ( 11 ) of the casing ( 10 ).
  • This suction pipe ( 14 ) has its terminal end (the right end in the figure) open toward a space between the compression mechanism ( 20 ) and the electric motor ( 45 ) in the casing ( 10 ).
  • the drive shaft ( 40 ) is disposed on the vertical center line of the easing ( 10 ).
  • the drive shaft ( 40 ) is a crank shaft including a main shaft portion ( 41 ) and an eccentric portion ( 42 ).
  • the eccentric portion ( 42 ) has a smaller diameter than the main shaft portion ( 41 ), and is formed on the upper surface of the main shaft portion ( 41 ).
  • the eccentric portion ( 42 ) is eccentric from the axial center of the main shaft portion ( 41 ) by a predetermined dimension, and constitutes an eccentric pin.
  • a lower bearing holder ( 48 ) is fixed to a portion adjacent to the lower end of the body ( 11 ) of the casing ( 10 ). This lower bearing holder ( 48 ) rotatably supports the lower end of the main shaft portion ( 41 ) of the drive shaft ( 40 ) through a sliding bearing ( 48 a ).
  • the interior of the drive shaft ( 40 ) is provided with an oil supply passage ( 44 ) extending vertically.
  • the lower end of the main shaft portion ( 41 ) is provided with an oil supply pump ( 43 ).
  • This oil supply pump ( 43 ) sucks refrigerating machine oil from the bottom of the casing ( 10 ).
  • the refrigerating machine oil passes through the oil supply passage ( 44 ) of the drive shaft ( 40 ) to be supplied to the sliding portion of the compression mechanism ( 20 ) and the bearing of the drive shaft ( 40 ).
  • the electric motor( 45 ) is comprised of a stator ( 46 ) and a rotor ( 47 ).
  • the stator ( 46 ) is fixed to the body ( 11 ) of the casing ( 10 ).
  • the rotor ( 47 ) is coupled to the main shaft portion ( 41 ) of the drive shaft ( 40 ) to drive the drive shaft ( 40 ) in rotation.
  • the compression mechanism ( 20 ) includes a fixed scroll ( 21 ), an orbiting scroll ( 22 ), and a housing ( 23 ) fixing and supporting the fixed scroll ( 21 ).
  • the fixed scroll ( 21 ) and the orbiting scroll ( 22 ) respectively include spiral laps ( 21 b, 22 b ) meshing with each other on end plates ( 21 a, 22 a ).
  • the compression mechanism ( 20 ) is configured such that the orbiting scroll ( 22 ) rotates eccentrically relative to the fixed scroll ( 21 ).
  • the housing ( 23 ) is comprised of a main body (flange) ( 23 a ) and a bearing holder ( 23 b ).
  • the main body ( 23 a ) is formed to be vertically continuous with the bearing holder ( 23 b ), and the main body ( 23 a ) is fitted into and coupled to the body ( 11 ) of the casing ( 10 ).
  • the bearing holder ( 23 b ) has a smaller diameter than the main body ( 23 a ), and protrudes downward from the main body ( 23 a ).
  • the bearing holder ( 23 b ) rotatably supports the main shaft portion ( 41 ) of the drive shaft ( 40 ) through a sliding bearing ( 23 c ).
  • the fixed scroll ( 21 ) is comprised of a fixed end plate ( 21 a ), a fixed lap ( 21 b ), and an edge portion ( 21 c ).
  • the fixed end plate ( 21 a ) is formed to have a substantially disk shape.
  • the fixed lap ( 21 b ) stands near the middle portion of the lower surface of the fixed end plate 21 a ), and is integrally formed with the fixed end plate ( 21 a ).
  • the fixed lap ( 21 b ) is formed to have a spiral wall shape with a constant height.
  • the edge portion ( 21 c ) is a wall extending downward from the outer peripheral portion of the fixed end plate ( 21 a ), and has a lower surface overlapping with the upper surface of the main body ( 23 a ) of the housing ( 23 ) to be fixed to the housing ( 23 ).
  • the orbiting scroll ( 22 ) is comprised of an orbiting end plate ( 22 a ), an orbiting lap ( 22 b ), and a boss ( 22 c ).
  • the orbiting end plate ( 22 a ) is formed to have a substantially disk shape.
  • the orbiting lap ( 22 b ) stands on upper surface of the orbiting end plate ( 22 a ), and is integrally formed with the orbiting end plate ( 22 a ).
  • the orbiting lap ( 22 b ) is formed to have a spiral wall shape with a constant height, and to mesh with the fixed lap ( 21 b ) of the fixed scroll ( 21 ).
  • the upper end of the fixed end plate ( 21 a ) is provided with a depression ( 21 g ), and a discharge cover ( 27 ) is attached to the upper surface of the fixed end plate ( 21 a ) to cover the depression ( 21 g ).
  • a space where the depression ( 21 g ) is covered with the discharge cover ( 27 ) is a discharge chamber ( 28 ) communicating with the discharge pipe ( 15 ).
  • a middle lower portion of the fixed end plate a ) is provided with a discharge port ( 26 ) communicating with the discharge chamber ( 28 ), and the discharge port ( 26 ) communicates with a compression chamber formed between the fixed lap ( 21 b ) and the orbiting lap ( 22 b ).
  • both upper and lower spaces ( 16 ) and ( 17 ) of the housing ( 23 ) are low-pressure spaces filled with a low-pressure refrigerant.
  • the boss ( 22 c ) extends downwardly from the lower surface of the orbiting end plate ( 22 a ), and integrally formed with the orbiting end plate ( 22 a ).
  • the eccentric portion ( 42 ) of the drive shaft ( 40 ) is inserted into the boss ( 22 c ) through a sliding bearing ( 22 d ). Therefore, if the drive shaft ( 40 ) rotates, the orbiting scroll ( 22 ) revolves around the axial center of the main shaft portion ( 41 ).
  • the revolution radius of the orbiting scroll ( 22 ) is the same as the eccentricity of the eccentric portion ( 42 ), i.e., a distance from the axial center of the main shaft portion ( 41 ) to the axial center of the eccentric portion ( 42 ).
  • the orbiting end plate ( 22 a ) is disposed in a first recess ( 23 d ) provided to the upper end of the housing ( 23 ).
  • the boss ( 22 c ) is disposed in a second recess (a crank chamber) ( 23 e ) provided to the main body ( 23 a ) of the housing ( 23 ).
  • the Oldham ring ( 50 ) is disposed between the orbiting end plate ( 22 a ) and the housing ( 23 ) to prevent the orbiting scroll ( 22 ) from rotating on its axis.
  • FIG. 2 is a plan view illustrating a state in which the Oldham ring ( 50 ) is being attached to the housing ( 23 ) and FIG. 3 is a cross-sectional view taken along line III-III of FIG. 2 .
  • FIG. 4 is a plan view of the Oldham ring ( 50 ), and FIG. 5 is a cross-sectional view taken along line V-V of FIG. 4 .
  • the Oldham ring ( 50 ) is configured to be slidable on the housing ( 23 ), into which the drive shaft ( 40 ) is inserted, by a first key mechanism ( 51 ) in a first direction perpendicular to the axial center of drive shaft ( 40 ).
  • the orbiting scroll ( 22 ) meshes with the fixed scroll ( 21 ) fixed to the housing ( 23 ), and is configured to be slidable on the Oldham ring ( 50 ) by a second key mechanism ( 52 ) in a second direction perpendicular to the axial center of drive shaft ( 40 ).
  • the Oldham ring ( 50 ) has a ring portion ( 53 ).
  • the first key mechanism ( 51 ) is comprised of a first key ( 54 ) provided to the ring portion ( 53 ) and a first key groove ( 61 ) formed in the housing ( 23 ).
  • the second key mechanism ( 52 ) is comprised of a second key ( 55 ) provided to the ring portion ( 53 ) and a second key groove ( 62 ) formed in the orbiting scroll ( 22 ).
  • a reciprocating motion of the first key ( 54 ) in the first key groove ( 61 ) and a reciprocating motion of the second key ( 55 ) in the second key groove ( 62 ) are synthesized to allow the orbiting scroll ( 22 ) engaging with the second key ( 55 ) to rotate on its axis, not to revolve around the fixed scroll ( 21 ) fixed to the housing ( 23 ).
  • the first key ( 54 ) protrudes from the ring portion ( 53 ) of the Oldham ring ( 50 ) toward the housing ( 23 ) (away from the orbiting scroll ( 22 )), and further protrudes in a radially inward direction of the ring portion ( 53 ).
  • the housing ( 23 ) includes a main body ( 23 a ) that is a flange to which the fixed scroll ( 21 ) is fixed, and the main body ( 23 a ) includes: a facing portion ( 71 ) having a predetermined thickness and having an orbiting scroll facing surface ( 70 ) being in contact with and facing (sliding on) the orbiting scroll ( 22 ); and an annular opening ( 72 ) formed around the orbiting scroll facing surface ( 70 ) and movably housing the ring portion ( 53 ).
  • the first key groove ( 61 ) is provided to the back surface ( 71 a ) of the facing portion ( 71 ) (the surface opposite to the orbiting scroll facing surface ( 70 )) so as to extend radially inwardly from the annular opening ( 72 ).
  • the first key groove ( 61 ) is preferably a groove opened on the back surface of the main body ( 23 a ) that is the flange of the housing ( 23 ).
  • the first key groove ( 61 ) is supposed to be a groove opened on the back surface of the main body ( 23 a ), as illustrated in FIGS. 6 and 7 .
  • the orbiting scroll facing surface ( 70 ) is provided with a groove, i.e., a seal ring mounting groove ( 75 ) provided in a situation where a sealing ring is mounted to the orbiting scroll facing surface ( 70 ).
  • the first key ( 54 ) includes a pair of first keys ( 54 ) opposed to each other by 180° on the Oldham ring ( 50 ).
  • the second key ( 55 ) includes a pair of second keys ( 55 ) opposed to each other by 180° on the Oldham ring ( 50 ) so as to be at right angles with the first key ( 54 ).
  • the interval (A) between the pair of the first keys ( 54 ) is smaller than the outer diameter (B) of the facing portion ( 71 ) of the housing ( 23 ), and the thickness (C) of the ring portion ( 53 ) is larger than the thickness (D) of the facing portion ( 71 ) of the housing ( 23 ).
  • the back surface of the facing portion ( 71 ) is a tilted surface ( 71 a ) such that the thickness of the facing portion ( 71 ) increases toward the inner periphery of the facing portion ( 71 ).
  • one first key ( 54 ) is inserted into one first key groove ( 61 ) from the annular opening ( 72 ) while the Oldham ring ( 50 ) is tilted, allowing one first key ( 54 ) to engage with the back surface ( 71 a ) of the facing portion ( 71 ) as illustrated in FIG. 11 . Then, the other first key ( 54 ) is inserted into the other first key groove ( 61 ). This allows for attaching the Oldham ring ( 50 ) to the housing ( 23 ).
  • the drive shaft ( 40 ) rotates and the orbiting scroll ( 22 ) revolves relative to the fixed scroll ( 21 ).
  • the Oldham ring ( 50 ) prevents the fixed scroll ( 21 ) from rotating on its axis.
  • volume of the compression chambers ( 25 a. 25 b ) increase and decrease repeatedly and periodically.
  • the refrigerant in the refrigerant circuit is sucked from the suction pipe ( 14 ) through a suction passage (not shown) and the suction port ( 29 ) into the compression chambers ( 25 a, 25 b ) when the volume of a portion, communicating with the suction port ( 29 ), of the compression chambers ( 25 a, 25 b ) is increased, and the refrigerant in the refrigerant circuit is compressed and discharged from the discharge port ( 26 ) to the discharge chamber ( 28 ) when the volume of a portion in which a suction side is closed decreases.
  • the refrigerant in the discharge chamber ( 28 ) is supplied from the discharge pipe ( 15 ) to the condenser in the refrigerant circuit, and is circulated in the refrigerant circuit. Then, the refrigerant in the discharge chamber ( 28 ) is sucked into the scroll compressor ( 1 ), again.
  • the first key ( 64 ) protrudes from the ring portion ( 53 ) of the Oldham ring ( 50 ) toward the housing ( 23 ) and further protrudes in the radially inward direction of the ring portion ( 53 ). This can sufficiently increase the area of the sliding surface between the first key ( 54 ) and the first key groove ( 61 ) to reduce a contact pressure of the key sliding surface.
  • the first key ( 54 ) protrudes in the radially inward direction of the Oldham ring ( 50 ), and the outer periphery of the housing ( 23 ) does not have to be notched (see FIG. 20 ), and the moment of the first key ( 54 ) can be reduced.
  • the first key groove ( 61 ) is formed in the position adjacent to the back side of the orbiting scroll facing surface ( 70 ) (in the position adjacent to the back surface of the facing portion ( 71 )), and thus, even if a sealing ring (not illustrated) is used, the first key groove ( 61 ) does not hinder the formation of the sealing ring.
  • the pair of first keys ( 54 ) are opposed to each other by 180° on the Oldham ring ( 50 ) to satisfy the relationship such that the interval (A) between the pair of the first keys ( 54 ) is smaller than the outer diameter (B) of the facing portion ( 71 ) of the housing ( 23 ) and the thickness (C) of the ring portion ( 53 ) is larger than the thickness (D) of the facing portion ( 71 ) of the housing ( 23 ).
  • the Oldham ring ( 50 ) can be easily attached to the housing ( 23 ) along an oblique direction.
  • the back surface of the facing portion ( 71 ) is the tilted surface ( 71 a ), and thus, when the Oldham ring ( 50 ) is attached to the housing ( 23 ), the first key ( 54 ) can be easily inserted into the first key groove ( 61 ).
  • the first key ( 54 ) engages with the first key groove ( 61 ) opened on the back surface of the flange ( 23 a ) of the housing ( 23 ), allowing the Oldham ring ( 50 ) to operate.
  • the first key ( 64 ) protrudes from the ring portion ( 53 ) of the Oldham ring ( 50 ) toward the housing ( 23 ) and further protrudes in the radially inward direction of the ring portion ( 53 ).
  • This can sufficiently increase the area of the sliding surface between the first key ( 54 ) and the first key groove ( 61 ) to reduce a contact pressure of the key sliding surface. Therefore, this can contribute to preventing insufficient strength of the first key ( 54 ) of the Oldham ring ( 50 ).
  • the outer periphery of the housing ( 23 ) does not have to be notched, and the moment of the first key ( 54 ) can be reduced. Therefore, this can contribute to preventing the strength of the Oldham ring ( 50 ) from decreasing too much.
  • the first key groove ( 61 ) is formed in the position adjacent to the back side of the orbiting scroll facing surface ( 70 ) (in the position adjacent to the back surface of the facing portion ( 71 )), and thus, the first key groove ( 61 ) does not hinder the formation of the sealing ring (not illustrated). Therefore, this makes it possible to use the seal ring ( 50 ) in a configuration in which the first key ( 54 ) and the first key groove ( 61 ) engage with each other.
  • the interval (A) between the pair of the first keys ( 54 ) is smaller than the outer diameter (B) of the facing portion ( 71 ) of the housing ( 23 ), and the thickness (C) of the ring portion ( 53 ) is larger than the thickness (D) of the facing portion ( 71 ) of the housing ( 23 ).
  • the Oldham ring ( 50 ) can be easily attached to the housing ( 23 ) along an oblique direction. Accordingly, the Oldham ring ( 50 ) does not have to be made large, making it possible to reduce the size of the mechanism.
  • the back surface of the facing portion ( 71 ) is the tilted surface ( 71 a ), and thus, when the Oldham ring ( 50 ) is attached to the housing ( 23 ), the first key ( 54 ) can be easily inserted into the first key groove ( 61 ), improving ease of attachment.
  • the first key groove ( 61 ) which is a groove opened on the back surface of the main body (flange) ( 23 a ) of the housing ( 23 ), can be easily formed.
  • the facing portion ( 71 ) may have a plate shape with a constant thickness. Such a configuration also allows for easily forming the first key groove ( 61 ) in the main body ( 23 a ) of the housing ( 23 ), and easily mounting the first key ( 54 ) in the first key groove ( 61 ).
  • the facing portion ( 71 ) may be configured as a separate member fixed to the main body ( 23 a ) of the housing ( 23 ). Such a configuration also allows for easily forming the first key groove ( 61 ) in the main body ( 23 a ) of the housing ( 23 ), and easily mounting the first key ( 54 ) in the first key groove ( 61 ).
  • the first key groove ( 61 ) may be a groove opened on the outer peripheral surface of the main body (flange) ( 23 a ) of the housing ( 23 ).
  • the groove opened on the outer peripheral surface of the main body (flange) ( 23 a ) of the housing ( 23 ) which functions as first key groove ( 61 ) can be easily formed.
  • the interval (A) between the pair of the first keys ( 54 ) is set to be smaller than the outer diameter (B) of the facing portion ( 71 ) of the housing ( 23 ), and the thickness (C) of the ring portion ( 53 ) is set to be larger than the thickness (D) of the facing portion( 71 ) of the housing ( 23 ).
  • these elements do not necessarily have to be set as described above.
  • oil may remain in the first key groove ( 61 ) to prevent the first key ( 54 ) from moving smoothly. It is therefore suitable that the housing ( 23 ) is provided with an oil removing hole for removing oil from the first key groove ( 61 ),
  • the orbiting scroll facing surface ( 70 ) of the facing portion ( 71 ) of the housing ( 23 ) is in contact with and faces the orbiting end plate ( 22 a ) of the orbiting scroll ( 22 ) to slide on the orbiting end plate ( 22 a ).
  • the sealing ring ( 76 ) may be mounted in the sealing ring mounting groove ( 75 ) to allow the orbiting scroll facing surface ( 70 ) to be spaced apart from and face the orbiting end plate ( 22 a ) of the orbiting scroll ( 22 ), and thus, the orbiting scroll facing surface ( 70 ) may be a surface not sliding on the orbiting end plate ( 22 a ). Even if the orbiting scroll facing surface ( 70 ) is not the surface sliding on the orbiting scroll ( 22 ), the above configuration of the present disclosure allows the first key groove ( 61 ) not to hinder the formation of the sealing ring (not illustrated).
  • the present disclosure is useful for, in a scroll compressor provided with a compression mechanism having a fixed scroll and an orbiting scroll, a structure of allowing the compression mechanism to hold an Oldham ring that is a mechanism preventing the orbiting scroll from rotating on its axis.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
US16/065,958 2015-12-28 2016-11-09 Scroll compressor Abandoned US20190017506A1 (en)

Applications Claiming Priority (3)

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JP2015-256983 2015-12-28
JP2015256983A JP6098706B1 (ja) 2015-12-28 2015-12-28 スクロール圧縮機
PCT/JP2016/083242 WO2017115559A1 (ja) 2015-12-28 2016-11-09 スクロール圧縮機

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JP (1) JP6098706B1 (zh)
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JP7014544B2 (ja) * 2017-08-02 2022-02-01 三菱重工サーマルシステムズ株式会社 オルダムリング、スクロール圧縮機
CN110439809A (zh) * 2019-09-02 2019-11-12 珠海格力节能环保制冷技术研究中心有限公司 装配结构及涡旋压缩机

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US4730998A (en) * 1985-09-27 1988-03-15 Mitsubishi Denki Kabushiki Kaisha Scroll-type apparatus having a pivoting main journal bearing
US4740143A (en) * 1985-05-16 1988-04-26 Mitsubishi Denki Kabushiki Kaisha Scroll-type fluid transferring machine with gap adjustment between scroll members
US4815951A (en) * 1986-05-08 1989-03-28 Mitsubishi Denki Kabushiki Kaisha Scroll compressor with super-charging tube
US4874302A (en) * 1987-07-08 1989-10-17 Mitsubishi Denki Kabushiki Kaisha Scroll compressor with oil feeding passages in thrust bearing

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JPS63138181A (ja) 1986-11-27 1988-06-10 Mitsubishi Electric Corp スクロ−ル圧縮機
JP2939958B2 (ja) * 1993-09-03 1999-08-25 株式会社富士通ゼネラル スクロール圧縮機
JPH0821377A (ja) * 1994-07-11 1996-01-23 Hitachi Ltd スクロール流体機械
JPH08312541A (ja) * 1995-05-19 1996-11-26 Mitsubishi Heavy Ind Ltd スクロール型流体機械
US6231324B1 (en) * 2000-02-02 2001-05-15 Copeland Corporation Oldham coupling for scroll machine
JP2008101599A (ja) * 2006-09-21 2008-05-01 Daikin Ind Ltd 自転防止部材、スクロール圧縮機、および可動スクロール部品
JP2010190167A (ja) * 2009-02-20 2010-09-02 Sanyo Electric Co Ltd スクロール型圧縮機
JP5282764B2 (ja) 2010-06-04 2013-09-04 ダイキン工業株式会社 スクロール圧縮機
CN103075341B (zh) * 2011-10-26 2015-10-07 艾默生环境优化技术(苏州)有限公司 压缩机
FR3000143B1 (fr) * 2012-12-21 2018-11-09 Danfoss Commercial Compressors Compresseur a spirales ayant des premier et second joints de oldham

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4702682A (en) * 1984-03-30 1987-10-27 Mitsubishi Denki Kabushiki Kaisha Motor driven scroll-type machine with compact oil lubricating structure
US4740143A (en) * 1985-05-16 1988-04-26 Mitsubishi Denki Kabushiki Kaisha Scroll-type fluid transferring machine with gap adjustment between scroll members
US4730998A (en) * 1985-09-27 1988-03-15 Mitsubishi Denki Kabushiki Kaisha Scroll-type apparatus having a pivoting main journal bearing
US4815951A (en) * 1986-05-08 1989-03-28 Mitsubishi Denki Kabushiki Kaisha Scroll compressor with super-charging tube
US4874302A (en) * 1987-07-08 1989-10-17 Mitsubishi Denki Kabushiki Kaisha Scroll compressor with oil feeding passages in thrust bearing

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CN108368847B (zh) 2020-04-24
EP3385538A4 (en) 2019-05-29
CN108368847A (zh) 2018-08-03
EP3385538A1 (en) 2018-10-10
EP3385538B1 (en) 2020-04-01
JP6098706B1 (ja) 2017-03-22
JP2017120055A (ja) 2017-07-06
WO2017115559A1 (ja) 2017-07-06

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