US20070081904A1 - Variable displacement type compressor - Google Patents

Variable displacement type compressor Download PDF

Info

Publication number
US20070081904A1
US20070081904A1 US10/570,482 US57048204A US2007081904A1 US 20070081904 A1 US20070081904 A1 US 20070081904A1 US 57048204 A US57048204 A US 57048204A US 2007081904 A1 US2007081904 A1 US 2007081904A1
Authority
US
United States
Prior art keywords
swash plate
outer circumferential
drive shaft
piston
center position
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
US10/570,482
Other languages
English (en)
Inventor
Hajime Kurita
Takayuki Imai
Masakazu Murase
Tetsuhiko Furanuma
Masaki Ota
Fuminobu Enokijima
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
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 Toyota Industries Corp filed Critical Toyota Industries Corp
Assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI reassignment KABUSHIKI KAISHA TOYOTA JIDOSHOKKI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ENOKIJIMA, FUMINOBU, FUKANUMA, TETSUHIKO, IMAI, TAKAYUKI, KURITA, HAJIME, MURASE, MASAKAZU, OTA, MASAKI
Publication of US20070081904A1 publication Critical patent/US20070081904A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the present invention relates to a variable displacement swash plate type compressor that forms, for example, part of a refrigeration circuit and compresses refrigerant gas.
  • such a swash plate type compressor includes a swash plate 92 , which is coupled to a drive shaft 91 to be rotatable integrally with the drive shaft 91 .
  • Single head pistons 94 are coupled to the outer circumferential portion of the swash plate 92 with pairs of semispherical shoes 93 A, 93 B. Therefore, when the swash plate 92 is rotated by rotation of the drive shaft 91 , the swash plate 92 slides with respect to the shoes 93 A, 93 B causing the pistons 94 to reciprocate, thereby compressing refrigerant gas.
  • Each pair of shoes 93 A, 93 B rotates about an axis S (a line that passes through the center of curvature P of the spherical surface and is perpendicular to sliding surfaces with respect to the swash plate 92 ) as the shoes 93 A, 93 B rotate relative to the swash plate 92 .
  • the rotation of the shoes 93 A, 93 B about the axis S is caused because a rotational force is applied to the shoes 93 A, 93 B in one direction about the axis S due to the difference between the circumferential velocities of the inner and outer circumferences of the swash plate 92 . More specifically, the circumferential velocity of the outer circumference of the swash plate 92 is greater than that of the inner circumference of the swash plate 92 .
  • the swash plate type compressor shown in FIG. 9 is configured such that the shoes 93 A, 93 B directly slide against the swash plate 92 . Therefore, the shoes 93 A, 93 B are unnecessarily rotated about the axis S due to the sliding motion caused as the shoes 93 A, 93 B rotate relative to the swash plate 92 . This increases the mechanical loss particularly at the sliding portion between each piston 94 and the corresponding shoe 93 B that receives reactive force of compression, and causes problems such as seizure at the sliding portions.
  • an annular step 90 a is provided at the center of a rear surface (a surface facing rightward in FIG. 10 ) of a swash plate (hereinafter, referred to as a first swash plate 90 ).
  • An annular sliding plate (hereinafter, referred to as a second swash plate 95 ) is arranged outward of the step 90 a of the first swash plate 90 .
  • the second swash plate 95 is supported to be coaxial with and rotatable relative to the first swash plate 90 .
  • the outer circumferential portion of the second swash plate 95 is arranged between the first swash plate 90 and the second shoes 93 B to be slidable with respect to the first swash plate 90 and the second shoes 93 B.
  • the first swash plate 90 slides relative to the second swash plate 95 , which reduces the rotation speed of the second swash plate 95 as compared to the rotation speed of the first swash plate 90 .
  • the rotation of each second shoe 93 B about the axis S caused by the relative rotation of the second swash plate 95 and the second shoes 93 B is suppressed, which suppresses mechanical loss and occurrence of problems.
  • a configuration has also been proposed in which rolling elements are provided between the first shoes 93 A and the second shoes 93 B and between the first swash plate 90 and the second swash plate 95 (for example, patent document 2).
  • a race of a thrust bearing arranged toward the second shoe 93 B can be considered as the second swash plate 95 .
  • the first swash plate 90 reliably slides with respect to the second swash plate 95 , which significantly reduces the relative rotation speed of the second swash plate 95 and the second shoes 93 B as compared to the relative rotation speed of the second shoes 93 B and the first swash plate 90 .
  • the first swash plate 90 which tilts with respect to the drive shaft 91 , has a salient corner 90 b at the outer circumferential edge portion corresponding to the vicinity of the piston 94 located at the top dead center position (the state shown in FIG. 10 ).
  • the salient corner 90 b is provided at the outer circumferential edge portion opposite to the second swash plate 95 and significantly protrudes in the radial direction (upward in the drawing) of the drive shaft 91 .
  • the second swash plate 95 which tilts with respect to the drive shaft 91 , has a salient corner 95 b at the outer circumferential edge portion corresponding to the vicinity of the piston 94 located at the bottom dead center position (not shown).
  • the salient corner 95 b is provided at the outer circumferential edge portion opposite to the first swash plate 90 and significantly protrudes in the radial direction of the drive shaft 91 .
  • the radii of the first swash plate 90 and the second swash plate 95 are reduced to avoid interference of the salient corners 90 b , 95 b with the pistons 94 .
  • Patent Document 1 Japanese Laid-Open Patent Publication No. 8-338363 (page 4, FIG. 1)
  • Patent Document 2 Japanese Laid-Open Patent Publication No. 8-28447 (page 3, FIG. 1)
  • variable displacement swash plate type compressor that improves the durability of a swash plate and shoes while suppressing reduction in the durability of pistons and enlargement of the pistons.
  • the present invention provides a variable displacement swash plate type compressor.
  • a swash plate is coupled to a drive shaft to be rotatable integrally with the drive shaft.
  • Pistons are coupled to the swash plate via shoes. Rotation of the drive shaft rotates the swash plate, which causes the pistons to reciprocate and compress gas. The displacement is changed by varying the inclination angle of the swash plate.
  • An inclined surface is provided at part of the entire outer circumferential edge portion of the swash plate.
  • part of the outer circumferential edge portion of the swash plate corresponding to the piston located at the top dead center position is provided with the inclined surface on a salient corner opposite to the piston. That is, part of the outer circumferential edge portion of the swash plate corresponding to a circumferential range of the swash plate that arranges any of the pistons at the top dead center position is provided with the inclined surface on the salient corner opposite to the piston.
  • the salient corner opposite to the piston significantly projects in the radial direction of the drive shaft when the swash plate tilts with respect to the drive shaft. Therefore, a significant reaction force of compression applied to the swash plate via the shoe of the piston located in the vicinity of the top dead center position is received in a suitable manner. This improves the durability of the swash plate and the shoes.
  • part of the outer circumferential edge portion of the swash plate corresponding to the piston located at the bottom dead center position is provided with the inclined surface on a salient corner toward the piston. That is, part of the outer circumferential edge portion of the swash plate corresponding to a circumferential range of the swash plate that arranges any of the pistons at the bottom dead center position is provided with the inclined surface on the salient corner toward the piston.
  • the salient corner toward the piston significantly projects in the radial direction of the drive shaft. Therefore, chamfering the projecting portion of the swash plate permits the diameter of the first swash plate to be increased while suppressing decrease of the durability and enlargement of the pistons.
  • the swash plate includes a first swash plate, which is coupled to the drive shaft to be rotatable integrally with the drive shaft, and a second swash plate, which is supported by the first swash plate.
  • the pistons are coupled to the first and second swash plates via first shoes, which abut against the first swash plate, and second shoes, which abut against the second swash plate and receive a reaction force of compression.
  • Part of the outer circumferential edge of the first swash plate corresponding to the piston located at the top dead center position is provided with the inclined surface on a salient corner opposite to the second swash plate.
  • part of the outer circumferential edge portion of the first swash plate corresponding to a circumferential range of the first swash plate that arranges any of the pistons at the top dead center position is provided with the inclined surface on the salient corner opposite to the first swash plate.
  • the salient corner opposite to the second swash plate significantly projects in the radial direction of the drive shaft when the first swash plate tilts with respect to the drive shaft. Therefore, chamfering the projecting portion of the first swash plate permits the diameter of the first swash plate to be increased while suppressing decrease of the durability and enlargement of the pistons. Therefore, the first swash plate supports the second swash plate in a suitable manner, and a great reaction force of compression applied to the second swash plate via the second shoe of the piston located in the vicinity of the top dead center position is received by the first swash plate via the second swash plate in a suitable manner. This improves the durability of the second swash plate and the second shoes.
  • part of the outer circumferential edge portion of the first swash plate corresponding to the piston located at the bottom dead center position is provided with the inclined surface on a salient corner toward the second swash plate. That is, part of the outer circumferential edge portion of the first swash plate corresponding to a circumferential range of the first swash plate that arranges any of the pistons at the bottom dead center position is provided with the inclined surface on the salient corner toward the second swash plate.
  • the salient corner toward the piston significantly projects in the radial direction of the drive shaft. Therefore, chamfering the projecting portion of the swash plate permits the diameter of the first swash plate to be increased while suppressing decrease of the durability and enlargement of the pistons.
  • the gas is refrigerant used in a refrigeration circuit, and carbon dioxide is used as the refrigerant.
  • FIG. 1 is a longitudinal cross-sectional view illustrating a variable displacement swash plate type compressor according to a first embodiment of the present invention
  • FIG. 2 is an enlarged partial view of FIG. 1 with the first and second swash plates not being sectioned;
  • FIG. 3 is a longitudinal cross-sectional view illustrating a variable displacement swash plate type compressor according to a second embodiment of the present invention
  • FIG. 4 is an enlarged partial view of FIG. 3 with the first and second swash plates not being sectioned (partially cut away) and part of the first and second shoes being sectioned;
  • FIG. 5 is an enlarged partial view illustrating a swash plate configuration according to a third embodiment of the present invention.
  • FIG. 6 is a longitudinal cross-sectional view illustrating a variable displacement swash plate type compressor according to a fourth embodiment of the present invention.
  • FIG. 7 is a cross-sectional view taken along line A-A of FIG. 6 ;
  • FIG. 8 is an enlarged partial cross-sectional view of FIG. 6 ;
  • FIG. 9 is a longitudinal cross-sectional view illustrating a prior art variable displacement swash plate type compressor.
  • FIG. 10 is a partial cross-sectional view illustrating a prior art technique.
  • variable displacement swash plate type compressor forms part of a refrigeration circuit of a vehicle air-conditioning system.
  • the first embodiment will be described with reference to FIGS. 1 and 2 .
  • FIG. 1 is a longitudinal cross-sectional view of the variable displacement swash plate type compressor (hereinafter, simply referred to as the compressor) 10 .
  • the left end of the compressor 10 in FIG. 1 is defined as the front of the compressor 10
  • the right end is defined as the rear of the compressor 10 .
  • a housing of the compressor 10 includes a cylinder block 11 , a front housing member 12 secured to the front end of the cylinder block 11 , and a rear housing member 14 secured to the rear end of the cylinder block 11 with a valve plate assembly 13 in between.
  • the cylinder block 11 and the front housing member 12 define a crank chamber 15 .
  • a drive shaft 16 is rotatably arranged between the cylinder block 11 and the front housing member 12 and extends through the crank chamber 15 .
  • the drive shaft 16 is coupled to a power source of the vehicle, which is an engine E in this embodiment, through a clutchless type power transmission mechanism PT, which constantly transmits power. Therefore, the drive shaft 16 is always rotated by the power supply from the engine E when the engine E is running.
  • a rotor 17 is coupled to the drive shaft 16 and is located in the crank chamber 15 .
  • the rotor 17 rotates integrally with the drive shaft 16 .
  • the crank chamber 15 accommodates a substantially disk-like first swash plate 18 .
  • a through hole 18 a is formed at the center of the first swash plate 18 .
  • the drive shaft 16 is inserted through the through hole 18 a of the first swash plate 18 .
  • the first swash plate 18 is supported by the drive shaft 16 via the through hole 18 a to be slidable and tiltable with respect to the drive shaft 16 .
  • a hinge mechanism 19 is located between the rotor 17 and the first swash plate 18 .
  • the hinge mechanism 19 includes two rotor protrusions 41 (one of the protrusions 41 located toward the front of the sheet of FIG. 1 is not shown), which protrude from the rear surface of the rotor 17 , and a swash plate protrusion 42 , which protrudes from the front surface of the first swash plate 18 toward the rotor 17 .
  • the distal end of the swash plate protrusion 42 is inserted between the two rotor protrusions 41 . Therefore, rotational force of the rotor 17 is transmitted to the first swash plate 18 via the rotor protrusions 41 and the swash plate protrusion 42 .
  • a substantially cylindrical support portion 39 projects at the center of the rear surface of the first swash plate 18 to surround the drive shaft 16 .
  • a disk-like second swash plate 51 is arranged outward of the support portion 39 of the first swash plate 18 .
  • a support hole 51 a is formed at the center of the second swash plate 51 .
  • the support portion 39 is inserted in the support hole 51 a .
  • the radius of the second swash plate 51 is substantially the same as that of the first swash plate 18 .
  • a radial bearing 52 is provided between the outer circumferential surface of the support portion 39 and the inner circumferential surface of the support hole 51 a of the second swash plate 51 .
  • a thrust bearing 53 is provided between the rear surface of the first swash plate 18 and the front surface of the second swash plate 51 .
  • the thrust bearing 53 has rolling elements, which are rollers 53 a in this embodiment, and the rollers 53 a are rotatably held by a retainer 53 b.
  • the second swash plate 51 is supported by the first swash plate 18 (the support portion 39 ) via the radial bearing 52 and the thrust bearing 53 such that the second swash plate 51 rotates relative to and tilt integrally with the first swash plate 18 .
  • a cam portion 43 is formed at the proximal end of the rotor protrusions 41 .
  • a cam surface 43 a is formed on the rear end face of the cam portion 43 facing the first swash plate 18 .
  • the distal end of the swash plate protrusion 42 slidably abuts against the cam surface 43 a of the cam portion 43 . Therefore, the hinge mechanism 19 guides the inclination of the first swash plate 18 and the second swash plate 51 as the distal end of the swash plate protrusion 42 moves toward and apart from the drive shaft 16 along the cam surface 43 a of the cam portion 43 .
  • Cylinder bores 22 are formed in the cylinder block 11 about the axis L of the drive shaft 16 at equal angular intervals and extend in the front-rear direction (left-right direction on the sheet of FIG. 1 ).
  • a single head piston 23 is accommodated in each cylinder bore 22 to be movable in the front-rear direction.
  • the front and rear openings of each cylinder bore 22 are closed by the front end face of the valve plate assembly 13 and the associated piston 23 .
  • Each cylinder bore 22 defines a compression chamber 24 .
  • the volume of each compression chamber 24 changes according to the reciprocation of the corresponding piston 23 .
  • Each piston 23 is formed by coupling, in the front-rear direction, a columnar head portion 37 , which is inserted in the associated cylinder bore 22 , and a neck 38 located in the crank chamber 15 outside the cylinder bore 22 .
  • the head portions 37 and the necks 38 are formed of an aluminum based metal material (pure aluminum or an aluminum alloy).
  • a pair of shoe seats 38 a are formed in each neck 38 .
  • Each neck 38 accommodates semispherical first and second shoes 25 A, 25 B.
  • the first shoe 25 A and the second shoe 25 B are formed of iron based metal material.
  • “semisphere” refers not only to a half of a sphere, but also to a shape that includes part of a spherical surface of a sphere.
  • the first shoe 25 A and the second shoe 25 B are each received by the corresponding shoe seat 38 a via a semispherical surface 25 a .
  • the semispherical surface 25 a of the first shoe 25 A and the semispherical surface 25 a of the second shoe 25 B are located on the same spherical surface defined about a point P.
  • Each piston 23 is coupled to the outer circumferential portion of the first swash plate 18 and the second swash plate 51 via the first shoe 25 A and the second shoe 25 B.
  • the first shoe 25 A located opposite to the compression chamber 24 abuts against the front surface of the first swash plate 18 via a planar sliding surface 25 b provided opposite to the semispherical surface 25 a .
  • the second shoe 25 B located toward the compression chamber 24 that is, the one that receives reaction force of compression abuts against the rear surface of the second swash plate 51 via a sliding surface 25 b provided opposite to the semispherical surface 25 a.
  • the radial bearing 52 and the thrust bearing 53 cause the first swash plate 18 to slide with respect to the second swash plate 51 .
  • each second shoe 25 B This suppresses the rotation of each second shoe 25 B about the axis S (a line that passes through the center of curvature point P of the semispherical surface 25 a and is perpendicular to the sliding surface 25 b ) caused by the relative rotation of the second swash plate 51 and the second shoe 25 B.
  • axis S a line that passes through the center of curvature point P of the semispherical surface 25 a and is perpendicular to the sliding surface 25 b
  • An intake chamber 26 and a discharge chamber 27 are defined between the valve plate assembly 13 and the rear housing member 14 in the housing of the compressor 10 .
  • the valve plate assembly 13 includes intake ports 28 and intake valves 29 located between the compression chambers 24 and the intake chamber 26 .
  • the valve plate assembly 13 also includes discharge ports 30 and discharge valves 31 located between the compression chambers 24 and the discharge chamber 27 .
  • refrigerant of the refrigeration circuit carbon dioxide is used.
  • Refrigerant gas introduced into the intake chamber 26 from an external circuit, which is not shown, is drawn into each compression chamber 24 via the associated intake port 28 and the intake valve 29 as the corresponding piston 23 moves from the top dead center position to the bottom dead center position.
  • the refrigerant gas that is drawn into the compression chamber 24 is compressed to a predetermined pressure as the piston 23 is moved from the bottom dead center position to the top dead center position, and is discharged to the discharge chamber 27 through the associated discharge port 30 and the discharge valve 31 .
  • the refrigerant gas in the discharge chamber 27 is then conducted to the external circuit.
  • a bleed passage 32 , a supply passage 33 , and a control valve 34 are provided in the housing of the compressor 10 .
  • the bleed passage 32 connects the crank chamber 15 to the intake chamber 26 .
  • the supply passage 33 connects the discharge chamber 27 to the crank chamber 15 .
  • the control valve 34 which is a conventional electromagnetic valve, is located in the supply passage 33 .
  • the opening degree of the control valve 34 is adjusted by controlling power supply from the outside to control the balance between the flow rate of highly pressurized discharge gas supplied to the crank chamber 15 through the supply passage 33 and the flow rate of gas conducted out of the crank chamber 15 through the bleed passage 32 .
  • the pressure in the crank chamber 15 is thus determined.
  • the difference between the pressure in the crank chamber 15 and the pressure in the compression chamber 24 is changed, which in turn varies the inclination angle of the first swash plate 18 and the second swash plate 51 . Accordingly, the stroke of each piston 23 , or the compressor displacement is adjusted.
  • the opening degree of the control valve 34 when the opening degree of the control valve 34 is reduced, the pressure in the crank chamber 15 is reduced. Therefore, the inclination angle of the first swash plate 18 and the second swash plate 51 increases, thereby increasing the stroke of each piston 23 . Thus, the displacement of the compressor 10 is increased.
  • the opening degree of the control valve 34 increases, the pressure in the crank chamber 15 is increased. Therefore, the inclination angle of the first swash plate 18 and the second swash plate 51 is reduced, thereby reducing the stroke of each piston 23 .
  • the displacement of the compressor 10 is reduced.
  • the support portion 39 of the first swash plate 18 supporting the second swash plate 51 is provided at a position decentered from the axis M 1 of the first swash plate 18 toward the piston 23 A located at the top dead center position.
  • the support portion 39 is provided at a position decentered toward a section of the first swash plate (toward the hinge mechanism 19 ) that causes any of the pistons 23 to be located at the top dead center position as viewed in the radial direction of the first swash plate 18 from the axis M 1 .
  • the second swash plate 51 , the radial bearing 52 , and the thrust bearing 53 are decentered from the first swash plate 18 toward the piston 23 A located at the top dead center position. Therefore, the axis M 2 of the second swash plate 51 , the radial bearing 52 , and the thrust bearing 53 is slightly displaced in parallel from the axis M 1 of the first swash plate 18 toward the center point P of the first shoe 25 A and the second shoe 25 B of the piston 23 A located at the top dead center position (for example, 0.05 to 5 mm, although the displacement is exaggerated in FIGS. 1 and 2 ).
  • part of the outer circumferential edge portion of the second swash plate 51 corresponding to the vicinity of the piston 23 A located at the top dead center position slightly protrudes in the radial direction of the first swash plate 18 from the outer circumferential edge portion of the first swash plate 18 . Therefore, for example, as compared to a case where the second swash plate 51 is not decentered from the first swash plate 18 , the contact area between the second shoe 25 B of the piston 23 located in the vicinity of the top dead center position and the second swash plate 51 is increased.
  • Part of the outer circumferential edge portion of the second swash plate 51 corresponding to the vicinity of the piston 23 B located at the bottom dead center position is located radially inward of the first swash plate 18 from the outer circumferential edge portion of the first swash plate 18 . That is, part of the outer circumferential edge portion of the second swash plate 51 corresponding to the vicinity of the hinge mechanism 19 is located radially inward of the first swash plate 18 than the outer circumferential edge portion of the first swash plate 18 .
  • the contact area between the second shoe 25 B of the piston 23 located in the vicinity of the bottom dead center position and the second swash plate 51 is reduced.
  • the reaction force of compression applied to the second shoe 25 B of the piston 23 located in the vicinity of the bottom dead center position is far smaller than the reaction force of compression applied to the second shoe 25 B of the piston 23 located in the vicinity of the top dead center position. Therefore, even if the contact area between the second shoe 25 B of the piston 23 located in the vicinity of the bottom dead center position and the second swash plate 51 is reduced, no problem arises in the durability of the second swash plate 51 and the second shoe 25 B.
  • Part of the outer circumferential edge portion of the first swash plate 18 corresponding to the piston 23 A located at the top dead center position and circumferentially adjacent parts thereof are provided with an inclined surface (a chamfer) on a salient corner 18 b opposite to the second swash plate 51 . That is, part of the outer circumferential edge portion of the second swash plate 51 corresponding to the vicinity of the hinge mechanism 19 is provided with the inclined surface (the chamfer) on the salient corner 18 b opposite to the second swash plate 51 .
  • part of the outer circumferential edge portion of the first swash plate 18 corresponding to a circumferential range of the first swash plate 18 that arranges any of the pistons 23 at the top dead center position is provided with the inclined surface on the salient corner 18 b opposite to the piston 23 A.
  • the inclined surface (the chamfer) on the salient corner 18 b is the largest at the part corresponding to the piston 23 A located at the top dead center position, and gradually becomes smaller along the circumferential direction.
  • the inclined surface (the chamfer) on the salient corner 18 b is provided within a range of quarter to half the circumference of the first swash plate 18 with the part corresponding to the piston 23 A located at the top dead center position arranged in the middle.
  • Part of the outer circumferential edge portion of the first swash plate 18 corresponding to the piston 23 B located at the bottom dead center position and circumferentially adjacent parts thereof are provided with an inclined surface (a chamfer) on a salient corner 18 c toward the second swash plate 51 . That is, part of the outer circumferential edge portion of the first swash plate 18 corresponding to a circumferential range of the first swash plate 18 that arranges the piston 23 B at the bottom dead center position is provided with the inclined surface on the salient corner 18 c opposite to the piston 23 B.
  • the inclined surface (the chamfer) is the largest at the part corresponding to the piston 23 B located at the bottom dead center position, and gradually becomes smaller along the circumferential direction.
  • the inclined surface (the chamfer) of the salient corner 18 c is provided within a range of quarter to half the circumference of the first swash plate 18 with the part corresponding to the piston 23 B located at the bottom dead center position arranged in the middle.
  • the inclined surface (the chamfer) on the salient corner 18 c is substantially the same size as the inclined surface (the chamfer) on the salient corner 18 b taking into consideration of the balance of the weight around the axis M 1 of the first swash plate 18 .
  • the first embodiment has the following advantages.
  • the second swash plate 51 is decentered from the first swash plate 18 toward the piston 23 A located at the top dead center position. Therefore, the contact area between the second shoe 25 B of the piston 23 located in the vicinity of the top dead center position and the second swash plate 51 is increased without increasing the diameter of the first swash plate 18 and the second swash plate 51 . Therefore, the second swash plate 51 reliably slides with respect to the second shoes 25 B, and the durability of the second swash plate 51 and the second shoes 25 B is improved while suppressing decrease of the durability and enlargement of the pistons 23 .
  • the thickness of the swash plate configuration between the first shoes 25 A and the second shoes 25 B is increased.
  • decentering the second swash plate 51 with respect to the first swash plate 18 to increase the contact area between the second shoe 25 B of the piston 23 located in the vicinity of the top dead center position and the second swash plate 51 is particularly effective in improving the durability of the second swash plate 51 and the second shoes 25 B while suppressing decrease of the durability and the enlargement of the pistons 23 .
  • Part of the outer circumferential edge portion of the first swash plate 18 corresponding to the piston 23 A located at the top dead center position is provided with the inclined surface on the salient corner 18 b opposite to the second swash plate 51 . Also, part of the outer circumferential edge portion of the first swash plate 18 corresponding to the piston 23 B located at the bottom dead center position is provided with the inclined surface on the salient corner 18 c toward the second swash plate 51 .
  • the salient corner 18 b opposite to the second swash plate 51 significantly projects in the radial direction of the drive shaft 16 when the first swash plate 18 tilts with respect to the drive shaft 16 .
  • the salient corner 18 c toward the second swash plate 51 significantly projects in the radial direction of the drive shaft 16 .
  • the first swash plate 18 supports the second swash plate 51 in a suitable manner, and a great reaction force of compression applied to the second swash plate 51 via the second shoe 25 B of the piston 23 located in the vicinity of the top dead center position is received by the first swash plate 18 via the second swash plate 51 in a suitable manner. This improves the durability of the second swash plate 51 .
  • carbon dioxide is used as the refrigerant of the refrigeration circuit.
  • the pressure in the refrigeration circuit becomes extremely high as compared to a case where chlorofluorocarbon refrigerant (for example, R134a) is used. Therefore, the reaction force of compression applied to the pistons 23 in the compressor is increased, which increases the pressure between the second swash plate 51 and the second shoes 25 B.
  • the first embodiment of the present invention is thus particularly effective in improving the durability of the second swash plate 51 and the second shoes 25 B while suppressing decrease of the durability and enlargement of the pistons 23 .
  • FIGS. 3 and 4 a second embodiment of the present invention will be described with reference to FIGS. 3 and 4 .
  • the second embodiment only differences from the first embodiment are explained.
  • Like or the same members are given the like or the same numbers and detailed explanations are omitted.
  • each first shoe 25 A located toward the hinge mechanism 19 , or opposite to the associated compression chamber 24 slidably abuts against the front surface of an outer circumferential portion 18 - 1 of the first swash plate 18 via the sliding surface 25 b opposite to the semispherical surface 25 a .
  • each second shoe 25 B located opposite to the hinge mechanism 19 , or toward the associated compression chamber 24 and receives the reaction force of compression slidably abuts against the rear surface of an outer circumferential portion 51 - 2 of the second swash plate 51 via the sliding surface 25 b opposite to the semispherical surface 25 a .
  • the center portion of the sliding surface 25 b of the first shoe 25 A bulges toward the first swash plate 18 (see FIG. 4 . The bulge is exaggerated in FIG. 4 ).
  • the sliding surface 25 b of the second shoe 25 B is flat.
  • a radial bearing 52 A which is a roller bearing, is located between the support portion 39 , which forms the inner circumferential portion of the first swash plate 18 , and an inner circumferential portion 51 - 1 of the second swash plate 51 , and more specifically, between the outer circumferential surface of the support portion 39 and the inner circumferential surface of the support hole 51 a of the second swash plate 51 .
  • the radial bearing 52 A includes an outer race 52 a attached to the inner circumferential surface of the support hole 51 a of the second swash plate 51 , an inner race 52 b attached to the outer circumferential surface of the support portion 39 of the first swash plate 18 , and rolling elements, which are rollers 52 c in the second embodiment.
  • the rollers 52 c are located between the outer race 52 a and the inner race 52 b.
  • the thrust bearing 53 which is a roller bearing, is located between the first shoes 25 A and the second shoes 25 B and between the outer circumferential portion 18 - 1 of the first swash plate 18 and the outer circumferential portion 51 - 2 of the second swash plate 51 .
  • the thrust bearing 53 has rolling elements, which are the rollers 53 a in the second embodiment, and the rollers 53 a are rotatably held by the retainer 53 b .
  • the thrust bearing 53 has an annular race 55 located between the rollers 53 a and the first swash plate 18 .
  • the race 55 is formed by carburizing and heat treating base material formed of mild steel such as SPC.
  • the corners at both ends of each roller 53 a are chamfered to prevent the second swash plate 51 and the race 55 from being damaged by the rollers 53 a abutting against the second swash plate 51 and the race 55 .
  • An annular engaging portion 18 d is provided on the rear surface of the first swash plate 18 at the outermost circumference of the outer circumferential portion 18 - 1 and projects toward the second swash plate 51 .
  • the race 55 is located inward of the engaging portion 18 d and is engaged with the first swash plate 18 at the radially outward edge of the race 55 by the abutment between the outer circumferential edge of the race 55 and the engaging portion 18 d .
  • the race 55 is guided by the engaging portion 18 d to rotate relative to the first swash plate 18 .
  • the second swash plate 51 is supported by the first swash plate 18 via the radial bearing 52 A and the thrust bearing 53 such that the second swash plate 51 rotates relative to and tilts integrally with the first swash plate 18 . Therefore, when the first swash plate 18 is rotated, the radial bearing 52 A and the thrust bearing 53 cause rolling motion between the first swash plate 18 and the second swash plate 51 . Therefore, the mechanical loss caused by sliding motion between the first swash plate 18 and the second swash plate 51 is converted to the mechanical loss caused by the rolling motion. This significantly suppresses the mechanical loss in the compressor.
  • the plate thickness Y 1 of the inner circumferential portion 51 - 1 of the second swash plate 51 that is supported by the radial bearing 52 A is greater than the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 that is supported by the thrust bearing 53 . More specifically, the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 is half or more of the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 and thinner than the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 . Also, the plate thickness Y 1 of the inner circumferential portion 51 - 1 of the second swash plate 51 is thicker than the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 .
  • the plate thickness of the inner circumferential portion 51 - 1 of the second swash plate 51 is designed to be greater than that of the outer circumferential portion 51 - 2 of the second swash plate 51 (Y 1 >Y 2 ) by providing a cylindrical first projection 56 , which projects toward the first swash plate 18 , and a cylindrical second projection 57 , which projects opposite to the first swash plate 18 .
  • the first projection 56 and the second projection 57 are arranged coaxial with the support hole 51 a , and the inner circumferential surfaces of the first projection 56 and the second projection 57 form part of the inner circumferential surface of the support hole 51 a .
  • the outer diameter Z 2 of the second projection 57 is smaller than the outer diameter Z 1 of the first projection 56 .
  • the outer circumferential corner 57 a of the distal end face of the second projection 57 is entirely chamfered to form a tapered face.
  • the second embodiment provides the following advantages in addition to the advantages of the first embodiment.
  • the thrust bearing 53 which supports the second swash plate 51 to be rotatable relative to the first swash plate 18 , is arranged between the first shoes 25 A and the second shoes 25 B and between the outer circumferential portion 18 - 1 of the first swash plate 18 and the outer circumferential portion 51 - 2 of the second swash plate 51 .
  • the radial bearing 52 A which supports the second swash plate 51 to be rotatable relative to the first swash plate 18 , is arranged between the inner circumferential portion (the support portion 39 ) of the first swash plate 18 and the inner circumferential portion 51 - 1 of the second swash plate 51 .
  • the thrust bearing 53 and the radial bearing 52 A effectively reduce the rotational resistance caused between the outer circumferential portion 18 - 1 of the first swash plate 18 and the outer circumferential portion 51 - 2 of the second swash plate 51 , and between the inner circumferential portion (the support portion 39 ) of the first swash plate 18 and the inner circumferential portion 51 - 1 of the second swash plate 51 . Therefore, even in the compressor 10 used for the refrigeration circuit that uses carbon dioxide as refrigerant, the sliding motion between the first swash plate 18 and the second swash plate 51 is converted to the mechanical loss caused by the rolling motion. As a result, problems such as the mechanical loss and the seizure are effectively suppressed.
  • the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 is half or more of the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 and thinner than the plate thickness X of the outer circumferential portion 18 - 1 .
  • a space between the first shoes 25 A and the second shoes 25 B is limited.
  • the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 needs to be reduced.
  • the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 is increased, the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 needs to be reduced.
  • the plate thicknesses X, Y 2 of the outer circumferential portions 18 - 1 , 51 - 2 of the first swash plate 18 and the second swash plate 51 need to be as thick as possible to secure the strength.
  • securing the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 to which power is transmitted from the drive shaft 16 should take precedence to securing the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 that is only required to slide with respect to the first swash plate 18 .
  • the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 is suitable to set the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 to be half or more of the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 and thinner than the plate thickness X of the outer circumferential portion 18 - 1 .
  • the plate thickness Y 1 of the inner circumferential portion 51 - 1 is greater than the plate thickness Y 2 of the outer circumferential portion 51 - 2 .
  • the thick inner circumferential portion 51 - 1 permits the second swash plate 51 to be stably supported by the radial bearing 52 A, and improves the sliding performance between the first swash plate 18 and the second swash plate 51 .
  • the outer circumferential portion 51 - 2 of the second swash plate 51 is relatively thinner than the inner circumferential portion 51 - 1 , the plate thickness of the outer circumferential portion 18 - 1 of the first swash plate 18 that is required to have a greater strength than the second swash plate 51 is easily secured.
  • the plate thickness Y 2 of the outer circumferential portion 51 - 2 of the second swash plate 51 is thinner than the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 . Therefore, the thin outer circumferential portion 51 - 2 of the second swash plate 51 facilitates securing the plate thickness of the outer circumferential portion 18 - 1 of the first swash plate 18 that is required to have a greater strength than the second swash plate 51 .
  • the plate thickness Y 1 of the inner circumferential portion 51 - 1 of the second swash plate 51 is greater than the plate thickness X of the outer circumferential portion 18 - 1 of the first swash plate 18 . Therefore, the radial bearing 52 A more stably supports the second swash plate 51 .
  • the outer diameter Z 2 of the second projection 57 is less than the outer diameter Z 1 of the first projection 56 .
  • part of the second projection 57 significantly approaches the piston 23 B located at the bottom dead center position.
  • the outer circumferential corner 57 a of the distal end face is chamfered.
  • part of the outer circumferential corner 57 a of the distal end face of the second projection 57 significantly approaches the piston 23 B located at the bottom dead center position. Therefore, it is effective to provide the chamfer on the outer circumferential corner 57 a of the distal end face of the second projection 57 in view of avoiding interference between the second swash plate 51 and the pistons 23 while increasing the plate thickness Y 1 of the inner circumferential portion 51 - 1 of the second swash plate 51 .
  • Part of the outer circumferential edge of the first swash plate 18 corresponding to the piston 23 A located at the top dead center position is provided with the inclined surface (the chamfer) on the salient corner 18 b opposite to the second swash plate 51 . Therefore, the first swash plate 18 and the second swash plate 51 can be enlarged while suppressing reduction in the durability and enlargement of the pistons 23 . Therefore, the second swash plate 51 reliably slides with respect to the second shoes 25 B, and the durability of the second swash plate 51 and the second shoes 25 B is improved while suppressing reduction in the durability and enlargement of the pistons 23 .
  • the salient corner 18 b (that has not been chamfered) opposite to the second swash plate 51 significantly projects in the radial direction of the drive shaft 16 when the first swash plate 18 tilts with respect to the drive shaft 16 .
  • the thickness of the necks 38 of the pistons 23 need to be reduced corresponding to the projecting portion, or the necks 38 need to be enlarged in the radial direction to avoid interference with the projecting portion.
  • reducing the thickness of the necks 38 leads to reduction in the durability of the pistons 23 , and enlargement of the necks 38 leads to enlargement of the compressor.
  • the radius of the first swash plate 18 may be reduced to avoid interference between the salient corner 18 b and the pistons 23 .
  • the radius of the second swash plate 51 which needs to be supported by the first swash plate 18 , must also be reduced. Therefore, in particular, the contact area between the second swash plate 51 and the second shoe 25 B of the piston 23 located in the vicinity of the top dead center position (in the compression stroke) that receives a significant reaction force of compression is reduced, which reduces the durability of the second swash plate 51 and the second shoes 25 B.
  • rollers 52 c are used as the rolling elements of the radial bearing 52 A.
  • the roller bearing that uses the rollers 52 c as the rolling elements has superior load bearing properties as compared to, for example, a case where balls are used as the rolling elements. This reduces the size of the radial bearing 52 A, which reduces the size of the compressor 10 .
  • the race 55 is located between the rollers 53 a of the thrust bearing 53 and the first swash plate 18 .
  • the race 55 is rotatable relative to the first swash plate 18 .
  • the engaging portion 18 d is provided on the outer circumferential portion 18 - 1 of the first swash plate 18 and extends toward the second swash plate 51 .
  • the race 55 is engaged with the first swash plate 18 by abutting against the engaging portion 18 d at the radially outward edge of the race 55 .
  • the engaging portion is provided at the inner circumferential portion of the first swash plate 18 and the race 55 is engaged with the first swash plate 18 at the radially inward edge
  • lubricant refrigerant oil
  • the engaging portion hinders the lubricant from entering between the first swash plate 18 and the race 55 .
  • the second embodiment in which the race 55 is engaged with the first swash plate 18 at the radially outward edge prevents the engaging portion 18 d from hindering the lubricant from entering between the first swash plate 18 and the race 55 .
  • the first swash plate 18 reliably slides with respect to the race 55 .
  • the engaging portion 18 d has an annular shape. Therefore, the engaging portion 18 d is stably engaged with the race 55 . Thus, the race 55 further reliably slides with respect to the first swash plate 18 .
  • the support portion 39 is not decentered from the axis M 1 of the first swash plate 18 . That is, the second swash plate 51 , the radial bearing 52 A (see FIG. 3 ), and the thrust bearing 53 (including the race 55 ) are not decentered from the first swash plate 18 .
  • the salient corner 18 c need not be chamfered as shown in FIG. 5 because the salient corner 18 c toward the second swash plate 51 does not significantly project in the radial direction from the second swash plate 51 .
  • the PCD of the thrust bearing 53 is greater than the diameter of an imaginary cylinder defined about the axes M 1 , M 2 of the first swash plate 18 and the second swash plate 51 and passes through the center points P of the first shoe 25 A and the second shoe 25 B.
  • the thrust bearing 53 (the rollers 53 a ) receives the reaction force of compression transmitted through the second swash plate 51 in a suitable manner, which improves the durability.
  • the “PCD” of the thrust bearing 53 refers to the diameter of an imaginary cylinder having the axis at the center of the thrust bearing 53 (at the axes M 1 , M 2 of the first swash plate 18 and the second swash plate 51 ) and passes through the mid point of the rotating axis of the rollers 53 a.
  • FIGS. 6 to 8 a fourth embodiment of the present invention will be described with reference to FIGS. 6 to 8 .
  • the fourth embodiment only differences from the first and second embodiments are explained. Like or the same members are given the like or the same numbers and detailed explanations are omitted.
  • the rotor 17 is fixed to the drive shaft 16 , and a swash plate 58 is supported on the drive shaft 16 .
  • the swash plate 58 is permitted to slide along and incline with respect to the drive shaft.
  • Coupling pieces 59 , 60 are fixed to the swash plate 58
  • guide pins 61 , 62 are fixed to the coupling pieces 59 , 60 .
  • a pair of guide holes 171 (only one is shown) is formed in the rotor 17 . Head portions of the guide pins 61 , 62 are slidably fitted to the guide holes 171 .
  • the engagement of the guide holes 171 with the guide pins 61 , 62 allows the swash plate 58 to incline with respect to the axial direction of the drive shaft 16 and rotate integrally with the drive shaft 16 .
  • the inclination of the swash plate 58 is guided by the guide holes 171 and the guide pins 61 , 62 , and the drive shaft 16 .
  • the coupling pieces 59 , 60 , the guide pins 61 , 62 , and the guide holes 171 form a hinge mechanism 19 A.
  • the swash plate 58 shown by a solid line in FIG. 6 is in the maximum inclination state of the swash plate 58 .
  • the swash plate 58 shown by a chain line in FIG. 6 is in the minimum inclination state.
  • Part of the outer circumferential edge portion of the swash plate 58 corresponding to the piston 23 A located at the top dead center position and circumferentially adjacent parts thereof are provided with an inclined surface on a salient corner 58 a opposite to the piston 23 . That is, part of the outer circumferential edge portion of the swash plate 58 corresponding to the vicinity of the hinge mechanism 19 A is provided with the inclined surface on the salient corner 58 a toward the hinge mechanism 19 A. In other words, part of the outer circumferential edge portion of the swash plate 58 corresponding to a circumferential range of the swash plate 58 that arranges the piston 23 A at the top dead center position is provided with the inclined surface on the salient corner 58 a opposite to the piston 23 . As shown in FIG. 7 , part of the inclined surface of the salient corner 58 a corresponding to the piston 23 located at the top dead center position is the largest, and gradually becomes smaller along the circumferential direction.
  • the inclined surface provided on the salient corner 58 a is located on the circumferential surface of an imaginary cylinder C having an axis M 3 that is parallel to the axis L of the drive shaft 16 .
  • the axis M 3 is displaced with respect to the axis L from the piston 23 A located at the top dead center position toward the drive shaft 16 .
  • the diameter of the imaginary cylinder C is greater than or equal to the diameter of the swash plate 58 .
  • the salient corner 58 a opposite to the piston 23 significantly projects in the radial direction of the drive shaft 16 when the swash plate 58 tilts with respect to the drive shaft 16 . Therefore, providing the inclined surface at the projecting portion (part of the salient corner 58 a ) of the swash plate 58 permits the swash plate 58 to be enlarged while suppressing reduction in the durability and enlargement of the pistons 23 . Therefore, a significant reaction force of compression applied to the swash plate 58 is received in a suitable manner via the second shoe 25 B of the piston 23 located in the vicinity of the top dead center position. This improves the durability of the swash plate 58 .
  • the radial bearing 52 may be omitted, and the second swash plate 51 may slide with respect to the support portion 39 .
  • the thrust bearing 53 may be omitted, and the second swash plate 51 may directly slide with respect to the first swash plate 18 .
  • the radial bearing 52 and the thrust bearing 53 may be omitted, and the second swash plate 51 may be secured to the first swash plate 18 so that the second swash plate 51 rotates integrally with the first swash plate 18 .
  • part of the outer circumferential edge portion of the second swash plate 51 corresponding to the piston 23 A located at the top dead center position is provided with an inclined surface (a chamfer) on the salient corner toward the first swash plate 18 .
  • part of the outer circumferential edge portion of the second swash plate 51 corresponding to the piston 23 B located at the bottom dead center position is provided with an inclined surface (a chamfer) on the salient corner opposite to the first swash plate 18 .
  • the inclined surfaces (the chamfers) at the projecting portions (part of the salient corners) of the second swash plate 51 permits the second swash plate 51 to be enlarged while suppressing reduction in the durability and enlargement of the pistons 23 . Therefore, the contact area between the second shoe 25 B of the piston 23 located in the vicinity of the top dead center position and the second swash plate 51 can further be increased, which further improves the durability of the second swash plate 51 and the second shoe 25 B.
  • the swash plate configuration to which the present invention may be applied is not limited to the one that uses the first swash plate and the second swash plate, but the swash plate configuration may include a number of swash plates such as three, four, or five swash plates.
  • the present invention may be applied to a variable displacement swash plate type compressor including double head pistons.
  • the second swash plate may be arranged on either the front or rear surfaces of the first swash plate, or may be arranged on each of the front and rear surfaces of the first swash plate.
  • the present invention need not be applied to the refrigerant compressor of the refrigeration circuit, but may be applied to, for example, an air-compressor.
  • the second embodiment may be modified such that, for example, the sliding surface 25 b of each first shoe 25 A is flat as shown in FIG. 5 .
  • the second embodiment may be modified such that, for example, the sliding surface 25 b of each second shoe 25 B is dented at the center as shown in FIG. 5 .
  • the weight of each second shoe 25 B, which reciprocate with the associated piston 23 is reduced, which reduces the inertial force of the second shoe 25 B. Therefore, the inclination angle of the first swash plate 18 and the second swash plate 51 , that is, the displacement of the compressor is smoothly changed.
  • the thrust bearing 53 may be changed to a roller bearing, which includes balls as the rolling elements.
  • the thrust bearing 53 may be changed to a sliding bearing.
  • the radial bearing 52 A only receives a radial load (a load perpendicular to the axis M 2 ) applied to the second swash plate 51 .
  • the rollers 52 c may be tilted with respect to the axis M 2 of the second swash plate 51 such that the radial bearing 52 A also receives a thrust load (a load along the axis M 2 ) in addition to the radial load.
  • the thrust bearing 53 only receives the thrust load applied to the second swash plate 51 .
  • the rollers 53 a may be tilted with respect to the surface of the second swash plate 51 such that the thrust bearing 53 also receives the radial load in addition to the thrust load.
  • the race 55 may be omitted, and the rollers 53 a of the thrust bearing 53 may roll directly on the first swash plate 18 .
  • the engaging portion 18 d may be omitted, and an engaging portion may be provided on the inner circumferential portion of the first swash plate 18 (for example, the proximal portion of the support portion 39 may serve also as the engaging portion) so that the race 55 is engaged with the first swash plate 18 on at radially inward edge.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US10/570,482 2003-09-02 2004-08-06 Variable displacement type compressor Abandoned US20070081904A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2003-310291 2003-09-02
JP2003310291 2003-09-02
JP2003-326962 2003-09-18
JP2003326962 2003-09-18
PCT/JP2004/011373 WO2005024233A1 (ja) 2003-09-02 2004-08-06 容量可変型斜板式圧縮機

Publications (1)

Publication Number Publication Date
US20070081904A1 true US20070081904A1 (en) 2007-04-12

Family

ID=34277688

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/570,482 Abandoned US20070081904A1 (en) 2003-09-02 2004-08-06 Variable displacement type compressor

Country Status (5)

Country Link
US (1) US20070081904A1 (ja)
EP (1) EP1669600A1 (ja)
JP (1) JPWO2005024233A1 (ja)
KR (1) KR20060057626A (ja)
WO (1) WO2005024233A1 (ja)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050147503A1 (en) * 2002-08-07 2005-07-07 Hajime Kurita Variable displacement compressor
US20110315006A1 (en) * 2010-05-27 2011-12-29 Heinrich Dueckinghaus Hydrostatic machine
WO2014190291A3 (en) * 2013-05-23 2015-04-30 Saham Gholamali Kyoumars Variable displacement devices and related methods
US20150167547A1 (en) * 2013-12-09 2015-06-18 Joachim Horsch Internal combustion engine
US11408407B2 (en) 2016-07-25 2022-08-09 Caire Inc. Wobble plate compressor and oxygen concentrator using the same

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009062856A (ja) * 2007-09-05 2009-03-26 Toyota Industries Corp 斜板式圧縮機

Citations (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6095761A (en) * 1997-05-26 2000-08-01 Zexel Corporation Swash plate compressor
US20010045158A1 (en) * 2000-05-24 2001-11-29 Keiji Shimizu Piston-type compressors with reciprocating pistons
US20020006336A1 (en) * 2000-07-14 2002-01-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate compressor having shoes made of a magnesium-based material
US20020067996A1 (en) * 2000-09-13 2002-06-06 Takahiro Sugioka Compressor part having sliding portion
US20020104432A1 (en) * 2000-12-12 2002-08-08 Toshihisa Shimo Compressor and sliding member thereof
US20020152888A1 (en) * 2001-04-20 2002-10-24 Manabu Sugiura Swash plate for compressor
US20020159895A1 (en) * 2001-02-28 2002-10-31 Manabu Sugiura Component having slide contact area of compressor
US6584886B2 (en) * 2000-07-26 2003-07-01 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor
US20030165389A1 (en) * 2002-03-01 2003-09-04 Visteon Global Technologies, Inc. Variable displacement compressor with stepped shaft
US20030202885A1 (en) * 2002-04-25 2003-10-30 Yukihiko Taguchi Variable displacement compressors
US6679077B2 (en) * 2001-07-26 2004-01-20 Kabushiki Kaisha Toyota Jidoshokki Piston type variable displacement fluid machine
US20040057840A1 (en) * 2002-09-25 2004-03-25 Tgk Co., Ltd. Capacity control valve for variable displacement compressor
US20040163533A1 (en) * 2003-02-21 2004-08-26 Shinji Tagami Swash plate-type compressor
US20040165993A1 (en) * 2003-02-21 2004-08-26 Denso Corporation Limiter device for variable displacement compressor
US20050145105A1 (en) * 2003-12-25 2005-07-07 Masaki Ota Swash plate compressor
US20050186086A1 (en) * 2004-02-24 2005-08-25 Masaki Ota Variable displacement compressor
US6988875B2 (en) * 2001-12-06 2006-01-24 Kabushiki Kaisha Toyota Jidoshokki Lubricating structure in fixed displacement piston type compressor
US7377754B2 (en) * 2003-04-14 2008-05-27 Kabushiki Kaisha Toyota Jidoshokki Compressor
US7406912B2 (en) * 2005-04-13 2008-08-05 Kabushiki Kaisha Toyota Jidoshokki Swash plate compressor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2590087Y2 (ja) * 1993-04-08 1999-02-10 サンデン株式会社 斜板式圧縮機
JPH0828447A (ja) * 1994-05-13 1996-01-30 Toyota Autom Loom Works Ltd ピストン式圧縮機における動力低減構造
JP2003003954A (ja) * 2001-06-21 2003-01-08 Sanden Corp 斜板式圧縮機

Patent Citations (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6095761A (en) * 1997-05-26 2000-08-01 Zexel Corporation Swash plate compressor
US20010045158A1 (en) * 2000-05-24 2001-11-29 Keiji Shimizu Piston-type compressors with reciprocating pistons
US20020006336A1 (en) * 2000-07-14 2002-01-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate compressor having shoes made of a magnesium-based material
US6582200B2 (en) * 2000-07-14 2003-06-24 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate compressor having shoes made of a magnesium-based material
US6584886B2 (en) * 2000-07-26 2003-07-01 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Compressor
US20020067996A1 (en) * 2000-09-13 2002-06-06 Takahiro Sugioka Compressor part having sliding portion
US6568918B2 (en) * 2000-09-13 2003-05-27 Kabushiki Kaisha Tokyo Jidoshokki Lubrication coating for the sliding portion of a swashplate compressor
US20020104432A1 (en) * 2000-12-12 2002-08-08 Toshihisa Shimo Compressor and sliding member thereof
US20020159895A1 (en) * 2001-02-28 2002-10-31 Manabu Sugiura Component having slide contact area of compressor
US20020152888A1 (en) * 2001-04-20 2002-10-24 Manabu Sugiura Swash plate for compressor
US6679077B2 (en) * 2001-07-26 2004-01-20 Kabushiki Kaisha Toyota Jidoshokki Piston type variable displacement fluid machine
US6988875B2 (en) * 2001-12-06 2006-01-24 Kabushiki Kaisha Toyota Jidoshokki Lubricating structure in fixed displacement piston type compressor
US20030165389A1 (en) * 2002-03-01 2003-09-04 Visteon Global Technologies, Inc. Variable displacement compressor with stepped shaft
US20030202885A1 (en) * 2002-04-25 2003-10-30 Yukihiko Taguchi Variable displacement compressors
US20040057840A1 (en) * 2002-09-25 2004-03-25 Tgk Co., Ltd. Capacity control valve for variable displacement compressor
US20040163533A1 (en) * 2003-02-21 2004-08-26 Shinji Tagami Swash plate-type compressor
US20040165993A1 (en) * 2003-02-21 2004-08-26 Denso Corporation Limiter device for variable displacement compressor
US7063003B2 (en) * 2003-02-21 2006-06-20 Sanden Corporation Swash plate-type compressor
US7377754B2 (en) * 2003-04-14 2008-05-27 Kabushiki Kaisha Toyota Jidoshokki Compressor
US20050145105A1 (en) * 2003-12-25 2005-07-07 Masaki Ota Swash plate compressor
US20050186086A1 (en) * 2004-02-24 2005-08-25 Masaki Ota Variable displacement compressor
US7406912B2 (en) * 2005-04-13 2008-08-05 Kabushiki Kaisha Toyota Jidoshokki Swash plate compressor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050147503A1 (en) * 2002-08-07 2005-07-07 Hajime Kurita Variable displacement compressor
US20110315006A1 (en) * 2010-05-27 2011-12-29 Heinrich Dueckinghaus Hydrostatic machine
US9074586B2 (en) * 2010-05-27 2015-07-07 Claas Selbstfahrende Erntemaschinen Gmbh Hydrostatic machine
WO2014190291A3 (en) * 2013-05-23 2015-04-30 Saham Gholamali Kyoumars Variable displacement devices and related methods
US20150167547A1 (en) * 2013-12-09 2015-06-18 Joachim Horsch Internal combustion engine
US9453459B2 (en) * 2013-12-09 2016-09-27 Joachim Horsch Internal combustion engine
US11408407B2 (en) 2016-07-25 2022-08-09 Caire Inc. Wobble plate compressor and oxygen concentrator using the same

Also Published As

Publication number Publication date
JPWO2005024233A1 (ja) 2006-11-02
KR20060057626A (ko) 2006-05-26
EP1669600A1 (en) 2006-06-14
WO2005024233A1 (ja) 2005-03-17

Similar Documents

Publication Publication Date Title
US9228573B2 (en) Wabble plate type variable displacement compressor
US5556261A (en) Piston type compressor
EP1533533A1 (en) Double-row ball bearing for supporting pulley
US20070081904A1 (en) Variable displacement type compressor
US9046089B2 (en) Wobble plate type variable displacement compressor
US7455008B2 (en) Swash plate compressor
US6393964B1 (en) Compressor having piston rotation restricting structure with lubricating inclined guide surface
US8997631B2 (en) Wobble plate-type variable displacement compressor
JP2005113907A (ja) 斜板式圧縮機
JP2006336562A (ja) 等速ジョイント及びそれを用いた揺動斜板型圧縮機
EP1087136B1 (en) Chamfered swash plate compressor piston head
KR100748140B1 (ko) 가변용량 사판식 압축기의 구동축 지지용 스러스트 베어링지지구조
JP4314405B2 (ja) 可変容量型斜板式圧縮機
EP1275846B1 (en) Hinge for a swash plate
JP2001032768A (ja) 可変容量型斜板式圧縮機
US20180051682A1 (en) Wobble Plate Type Variable Displacement Compressor
US20010042438A1 (en) Piston for swash plate type compressor
EP0856663A2 (en) Variable capacity swash plate compressor
EP1288496A2 (en) Piston type variable displacement compressor
JP2001159392A (ja) 斜板式圧縮機用の片頭ピストン
JP2005009526A (ja) スラストニードル軸受、ころ及びカーエアコン用コンプレッサ
JP2006009628A (ja) 可変容量圧縮機
JPH1089246A (ja) 圧縮機
JPH1077966A (ja) 可変容量型斜板式圧縮機
JP2003328931A (ja) 揺動斜板式圧縮機

Legal Events

Date Code Title Description
AS Assignment

Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KURITA, HAJIME;IMAI, TAKAYUKI;MURASE, MASAKAZU;AND OTHERS;REEL/FRAME:018423/0432

Effective date: 20060301

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION