WO2005024233A1 - Compresseur a plateau oscillant a deplacement variable - Google Patents

Compresseur a plateau oscillant a deplacement variable Download PDF

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Publication number
WO2005024233A1
WO2005024233A1 PCT/JP2004/011373 JP2004011373W WO2005024233A1 WO 2005024233 A1 WO2005024233 A1 WO 2005024233A1 JP 2004011373 W JP2004011373 W JP 2004011373W WO 2005024233 A1 WO2005024233 A1 WO 2005024233A1
Authority
WO
WIPO (PCT)
Prior art keywords
swash plate
piston
outer peripheral
dead center
shoe
Prior art date
Application number
PCT/JP2004/011373
Other languages
English (en)
Japanese (ja)
Inventor
Hajime Kurita
Takayuki Imai
Masakazu Murase
Tetsuhiko Fukanuma
Masaki Ota
Fuminobu Enokijima
Original Assignee
Kabushiki Kaisha Toyota Jidoshokki
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 Kabushiki Kaisha Toyota Jidoshokki filed Critical Kabushiki Kaisha Toyota Jidoshokki
Priority to US10/570,482 priority Critical patent/US20070081904A1/en
Priority to JP2005513610A priority patent/JPWO2005024233A1/ja
Priority to EP04771372A priority patent/EP1669600A1/fr
Publication of WO2005024233A1 publication Critical patent/WO2005024233A1/fr

Links

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 type swash plate type compressor that forms a refrigeration circuit and compresses refrigerant gas, for example.
  • a swash plate 92 is connected to a drive shaft 91 so as to be rotatable.
  • a single-headed piston 94 is moored around the outer periphery of the swash plate 92 via a pair of hemispherical shoes 93A and 93B. Accordingly, when the swash plate 92 is rotated by the rotation of the drive shaft 91, the swash plate 92 slides with respect to each of the shoes 93A and 93B, and the piston 94 reciprocates linearly to compress the refrigerant gas.
  • the shears 93A and 93B center on their own axis S (the line passing through the center of curvature P of the spherical surface and perpendicular to the sliding surface with the swash plate 92) in accordance with the relative rotation with the swash plate 92.
  • a rotational movement will be performed.
  • the rotation of the shafts 93A and 93B about the axis S is, as a whole, in one direction around the axis S with respect to the shafts 93A and 93B due to the difference in peripheral speed between the inner and outer peripheries of the swash plate 92 on the outer peripheral side. This is performed in a state equivalent to the application of a rotational force to the motor.
  • the swash plate type compressor shown in FIG. 9 has a configuration in which the shoes 93A and 93B slide directly on the swash plate 92. Therefore, the slides 93A and 93B had to wastefully perform the rotational movement about the axis S by sliding based on the relative rotation with the swash plate 92. Therefore, there is a problem in that mechanical loss is particularly large in a sliding portion between the piston 94 and the shoe 93B on the side receiving the compression reaction force, and problems such as seizure occur in the sliding portion. .
  • a step portion 90a is provided in the center of the rear surface of the swash plate (hereinafter referred to as a first swash plate 90) (facing surface on the right side in the drawing) in an annular shape.
  • a second swash plate 95 is supported so as to be rotatable relative to the first swash plate 90 at a coaxial position.
  • 2nd swashplate 95 The outer peripheral portion is slidably provided between the first swash plate 90 and the second shoe 93B between the first swash plate 90 and the second shoe 93B.
  • the first swash plate structure includes a first swash plate 93A and a second swash plate 93B. It becomes thicker. Therefore, the first swash plate 90 inclined with respect to the drive shaft 91 is provided at the outer peripheral edge corresponding to the vicinity of the piston 94 (the state in FIG. 10) at the top dead center position, on the side opposite to the second swash plate 95.
  • the convex corner portion 90b protrudes largely in the radial direction of the drive shaft 91 (upward in the drawing).
  • the second swash plate 95 inclined with respect to the drive shaft 91 has a convex portion on the opposite side to the first swash plate 90 at an outer peripheral edge corresponding to the vicinity of a piston 94 (not shown) at the bottom dead center position.
  • the corner portion 95b protrudes largely in the radial direction of the drive shaft 91.
  • Patent document 1 JP-A-8-338363 (page 4, FIG. 1)
  • Patent Document 2 JP-A-8-28447 (page 3, FIG. 1)
  • An object of the present invention is to provide a variable displacement type swash plate type compressor capable of improving the durability of a swash plate and a shroud while suppressing a decrease in the durability and an increase in size of a piston.
  • the invention provides a drive shaft, wherein a swash plate is integrally rotatably connected to the drive shaft, and a piston is moored to the swash plate via a shoe. With the rotation of the swash plate, the piston is reciprocated linearly to compress the gas, and the displacement is changed by changing the inclination angle of the swash plate.
  • the present invention provides a variable displacement type swash plate compressor in which an inclined surface is provided on a part of the entire outer peripheral edge of the swash plate.
  • the diameter of the swash plate can be increased while suppressing the decrease in the durability and the size of the piston. be able to. Therefore, a large compression reaction force acting on the swash plate via the shoe can be suitably received. This leads to improved durability of the swash plate and the shoe.
  • a slope corresponding to the piston located at the top dead center position is provided at an outer peripheral edge of the swash plate at a convex corner opposite to the piston.
  • an inclined surface is provided at a convex corner on the side opposite to the piston in a portion of an outer peripheral edge of the swash plate corresponding to a circumferential range of the swash plate in which the piston is disposed at the top dead center position.
  • a slope corresponding to the piston at the bottom dead center position is provided at a convex corner on the piston side at an outer peripheral edge of the swash plate. That is, at the outer peripheral edge of the swash plate corresponding to the circumferential range of the swash plate in which the piston is disposed at the bottom dead center position, a slope is provided at the convex corner on the piston side.
  • the convex portion on the piston side protrudes largely in the radial direction of the drive shaft. Therefore, by chamfering the protruding portion of the swash plate, it is possible to increase the diameter of the first swash plate while suppressing the decrease in the durability and the size of the piston.
  • the swash plate includes a first swash plate integrally rotatably connected to a drive shaft, and a second swash plate supported by the first swash plate.
  • a piston is moored to the second swash plate via a first shoe in contact with the first swash plate and a second shoe on a side receiving a compression reaction force in contact with the second swash plate.
  • On the outer peripheral edge of the first swash plate a portion corresponding to the piston at the top dead center position is provided with an inclined surface at a convex corner opposite to the second swash plate.
  • the slope is inclined to a convex corner opposite to the first swash plate.
  • the first swash plate inclined with respect to the drive shaft has a convex corner on the outer peripheral edge corresponding to the piston at the top dead center position, which is opposite to the second swash plate, in the radial direction of the drive shaft. It will protrude greatly toward it. Therefore, by chamfering the protruding portion of the first swash plate, it is possible to increase the diameter of the first swash plate while suppressing the durability and the size of the piston from being reduced. Therefore, the support of the second swash plate by the first swash plate is preferable, and the second shot of the piston near the top dead center position is suitable. A large compression reaction force acting on the second swash plate via the first swash plate can be suitably received by the first swash plate via the second swash plate. This leads to improved durability of the second swash plate and the second shoe.
  • a slope corresponding to the piston at the bottom dead center position is provided on the outer peripheral edge portion of the first swash plate at a convex corner on the second swash plate side. ing. That is, in the outer peripheral portion of the first swash plate corresponding to the circumferential range of the first swash plate in which the piston is arranged at the bottom dead center position, a slope is provided at the convex corner on the second swash plate side. ing.
  • the convex portion on the piston side protrudes largely in the radial direction of the drive shaft. Therefore, by chamfering the protruding portion of the swash plate, it is possible to increase the diameter of the first swash plate while suppressing the decrease in the durability and the size of the piston.
  • the gas is a refrigerant used in a refrigeration circuit, and carbon dioxide is used as the refrigerant.
  • FIG. 1 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a first embodiment of the present invention.
  • FIG. 2 is an enlarged view of a main part of FIG. 1, without a cross section of first and second swash plates.
  • FIG. 3 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a second embodiment of the present invention.
  • FIG. 4 is an enlarged view of a main part of FIG. 3, in which the first and second swash plates are not cross-sectioned (partially broken), and some of the first and second shows are cross-sections.
  • FIG. 5 is an enlarged view of a main part showing a swash plate structure according to a third embodiment of the present invention.
  • FIG. 6 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a fourth embodiment of the present invention.
  • FIG. 7 is a sectional view taken along line A—A in FIG. 6.
  • FIG. 8 is an enlarged sectional view of a main part of FIG. 6.
  • FIG. 9 is a longitudinal sectional view of a conventional variable displacement swash plate type compressor.
  • FIG. 10 is a partial sectional view showing a conventional technique.
  • FIG. 1 is a longitudinal sectional view of a variable capacity swash plate compressor (hereinafter simply referred to as a compressor 10).
  • a compressor 10 a variable capacity swash plate compressor
  • the left side is the front of the compressor
  • the right side is the rear of the compressor.
  • the housing of the compressor 10 includes a cylinder block 11, a front bar and a housing 12 joined and fixed to the front end of the cylinder block 11, and a valve port at the rear end of the cylinder block 11. And a rear housing 14 joined and fixed via a formed body 13.
  • a crank chamber 15 is defined between the cylinder block 11 and the front housing 12.
  • a drive shaft 16 is rotatably disposed between the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 15.
  • the drive shaft 16 is operatively connected via a power transmission mechanism PT of an engine E force clutchless type (constant transmission type) which is a traveling drive source of the vehicle. Therefore, during the operation of the engine E, the drive shaft 16 is constantly rotated by receiving the power supply from the engine E.
  • a rotor 17 is fixed to the drive shaft 16 in the crank chamber 15 so as to be able to rotate.
  • a first swash plate 18 having a substantially disk shape is accommodated.
  • a through hole 18a is formed.
  • the drive shaft 16 is passed through the through hole 18a of the first swash plate 18.
  • the first swash plate 18 is slidably and tiltably supported on the drive shaft 16 via a through hole 18a.
  • a hinge mechanism 19 is interposed between the rotor 17 and the first swash plate 18.
  • the hinge mechanism 19 includes two rotor-side projections 41 (one of which is not shown on the front side of the drawing) projecting from the rear surface of the rotor 17, and a rotor projection 41 on the front surface of the first swash plate 18. And a swash plate side projection 42 protruding toward the 17th side.
  • the swash plate side projection 42 has two It enters between the protrusions 41 on the data side. Therefore, the rotational force of the rotor 17 is transmitted to the first swash plate 18 via the rotor-side protrusion 41 and the swash-plate-side protrusion 42.
  • a substantially cylindrical support portion 39 is provided so as to surround the drive shaft 16.
  • a disc-shaped second swash plate 51 is disposed in a state where the support portion 39 is inserted through a support hole 51a formed through the center thereof. ing.
  • the second swash plate 51 one having a radius substantially equal to that of the first swash plate 18 is used.
  • a radial bearing 52 is interposed between the outer peripheral surface of the support portion 39 and the inner peripheral surface of the support hole 51a of the second swash plate 51.
  • a thrust bearing 53 is interposed 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 a plurality of rollers 53a as rolling elements, and the plurality of rollers 53a are rotatably held by a retainer 53b.
  • the second swash plate 51 is supported via the radial bearing 52 and the thrust bearing 53, so that the second swash plate 18 can be rotated relative to the first swash plate 18 and tilted integrally therewith. Supported by Part 39).
  • a cam portion 43 is formed at the base of the rotor-side projection 41.
  • a cam surface 43a is formed on a rear end surface of the cam portion 43 facing the first swash plate 18.
  • the tip of the swash plate side projection 42 is slidably abutted against the cam surface 43a of the force portion 43. Accordingly, the hinge mechanism 19 moves the first swash plate 18 and the second swash plate 51 by moving the tip of the swash plate-side protrusion 42 on the cam surface 43a of the cam portion 43 in the direction of contact with and separation from the drive shaft 16. Guide the tilt.
  • a plurality of cylinder bores 22 are formed in the cylinder block 11 around the axis L of the drive shaft 16 at equal angular intervals in the front-rear direction (lateral direction on the paper).
  • the single-headed piston 23 is accommodated in each cylinder bore 22 so as to be movable in the front-rear direction.
  • the front-rear opening of the cylinder bore 22 is closed by the front end face of the valve / port forming body 13 and the piston 23, and a compression chamber 24 whose volume changes in accordance with the movement of the piston 23 in the front-rear direction is defined in the cylinder bore 22. Have been.
  • the piston 23 has a cylindrical head 37 inserted into the cylinder bore 22 and a neck 38 located outside the cylinder bore 22 and located in the crank chamber 15 connected in the front-rear direction.
  • Head 37 The neck 38 is made of an aluminum-based metallic material (pure aluminum or an aluminum alloy). Inside the neck portion 38, a pair of shoe seats 38a are recessed. Inside the neck portion 38, a first show 25A and a second show 25B that form a hemisphere are provided.
  • the first shoe 25A and the second shoe 25B are made of an iron-based metal material.
  • the term “hemisphere” refers to a sphere having a part of the spherical surface, which does not mean only a bisected sphere.
  • the first shoe 25A and the second shoe 25B are each spherically received by the corresponding shoe seat 38a with a hemispherical surface 25a.
  • the hemispherical surface 25a of the first show 25A and the hemispherical surface 25a of the second show 25B exist on the same spherical surface with the point P as the center.
  • Each piston 23 is moored to the outer periphery of the first swash plate 18 and the second swash plate 51 via the first shower 25A and the second shower 25B.
  • the first shoe 25A located on the opposite side to the compression chamber 24 is in contact with the front surface of the first swash plate 18 with a planar sliding contact surface 25b on the opposite side to the hemispherical surface 25a.
  • the second shoe 25B on the compression chamber 24 side that is, on the side receiving the compression reaction force, is in contact with the rear surface of the second swash plate 51 with a sliding contact surface 25b opposite to the hemispheric surface 25a.
  • the piston 23 reciprocates linearly in the front-rear direction.
  • a slip occurs between the first swash plate 18 and the second swash plate 51 due to the action of the radial bearing 52 and the thrust bearing 53, and the rotation of the second swash plate 51
  • the speed is lower than the rotation speed of the first swash plate 18. Therefore, the relative rotation speed between the second swash plate 51 and the second swash plate 18 is lower than the relative rotation speed between the second swash plate 25B and the first swash plate 18.
  • the second shot centered on the axis S (the line passing through the center point P of curvature of the hemispherical surface 25a and perpendicular to the sliding surface 25b) caused by the relative rotation between the second swash plate 51 and the second shot 25B.
  • the rotation movement of the 25B can be suppressed, and the occurrence of mechanical loss and malfunction due to the rotation movement can be suppressed.
  • a suction chamber 26 and a discharge chamber 27 are separately formed between the valve / port forming body 13 and the rear housing 14.
  • the valve port forming body 13 is formed with a suction port 28 and a suction valve 29 so as to be located between the compression chamber 24 and the suction chamber 26.
  • the discharge port 30 and the discharge valve 31 are respectively formed in the valve port forming body 13 so as to be located between the compression chamber 24 and the discharge chamber 27.
  • Carbon dioxide is used as a refrigerant in the refrigeration circuit.
  • External circuit (not shown) Force Refrigerant gas introduced into the suction chamber 26 moves from the top dead center position to the bottom dead center position side of each piston 23, and is sucked into the compression chamber 24 via the suction port 28 and the suction valve 29. Is done.
  • the refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure by moving from the bottom dead center position of the piston 23 to the top dead center position side, and is discharged through the discharge port 30 and the discharge valve 31 to the discharge chamber 27. Is discharged.
  • the refrigerant gas in the discharge chamber 27 is led to an external circuit.
  • a bleed passage 32 In the housing of the compressor 10, a bleed passage 32, an air supply passage 33, and a control valve 34 are provided.
  • the bleed passage 32 connects the crank chamber 15 and the suction chamber 26.
  • the air supply passage 33 connects the discharge chamber 27 and the crank chamber 15.
  • a well-known control valve 34 composed of a solenoid valve is provided.
  • the opening of the control valve 34 By adjusting the opening of the control valve 34 by external power supply control, the amount of high-pressure discharge gas introduced into the crank chamber 15 through the air supply passage 33 and the crank through the bleed passage 32 The balance with the amount of gas led out from the chamber 15 is controlled, and the internal pressure of the crank chamber 15 is determined. The difference between the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 24 is changed in accordance with the change in the internal pressure of the crank chamber 15, and as a result, the inclination angles of the first swash plate 18 and the second swash plate 51 are changed. The stroke of the piston 23 or the displacement of the compressor is adjusted.
  • the support portion 39 that supports the second swash plate 51 in the first swash plate 18 is located at the top dead center with respect to the center axis Ml of the first swash plate 18. It is eccentrically provided on the piston 23A side at the position. Stated another way, the support portion 39 is provided eccentrically on the side (the hinge mechanism 19 side) that brings the piston 23 to the top dead center position when the radial direction of the first swash plate 18 is viewed from the center axis Ml. Has been. Therefore, the second swash plate 51, the radial bearing 52, and the thrust bearing 53 (retainer 53b) are located at the top dead center with respect to the first swash plate 18. It is eccentric to the piston 23A side.
  • the center axis M2 of the second swash plate 51, the radial bearing 52, and the thrust bearing 53 is, with respect to the center axis Ml of the first swash plate 18, the first shoe 25A of the piston 23A at the top dead center position and It is slightly parallel (for example, 0.055 mm; exaggerated in the drawing) to the center point P side of the second show 25B.
  • the portion corresponding to the vicinity of the piston 23 A at the top dead center position is from the outer peripheral edge of the first swash plate 18 in the radial direction of the first swash plate 18. Slightly protruding. Therefore, for example, compared to the case where the second swash plate 51 is not eccentric with respect to the first swash plate 18, the second show 25B of the piston 23 near the top dead center position and the second swash plate 51 The contact area is increasing.
  • the portion corresponding to the vicinity of the piston 23 B at the bottom dead center position has a larger diameter than the outer peripheral edge of the first swash plate 18. It will be located inside the direction. That is, the portion of the outer peripheral edge 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 from the outer peripheral edge of the first swash plate 18. Therefore, for example, as compared with the case where the second swash plate 51 is not eccentric with respect to the first swash plate 18, the second shoe 25B of the piston 23 near the bottom dead center position and the second swash plate 51 The contact area becomes smaller.
  • the compression reaction force acting on the second shoe 25B of the piston 23 near the bottom dead center position is much smaller than the compression reaction force acting on the second shoe 25B of the piston 23 near the top dead center position. Les ,. For this reason, even if the contact area between the second shoe 25B of the piston 23 near the bottom dead center position and the second swash plate 51 becomes smaller, there is no limitation on the durability of the second swash plate 51 and the second shoe 25B. No problem.
  • a portion corresponding to the piston 23A at the top dead center position and a portion located in front and rear of the portion in the circumferential direction are opposite to the second swash plate 51.
  • An inclined surface (chamfered) is provided on the convex corner portion 18b. That is, in the outer peripheral edge portion of the second swash plate 51 corresponding to the vicinity of the hinge mechanism 19, a slope (chamfer) is provided at the convex corner 18b opposite to the second swash plate 51.
  • the convex angle portion 18b opposite to the piston 23A is formed at the outer peripheral edge portion of the first swash plate 18 corresponding to the circumferential range of the first swash plate 18 in which the piston 23 is arranged at the top dead center position.
  • An inclined surface is provided at the outer peripheral edge portion of the first swash plate 18 corresponding to the circumferential range of the first swash plate 18 in which the piston 23 is arranged at the top dead center position.
  • An inclined surface is provided.
  • the slope (chamfer) of the convex corner 18b is The portion corresponding to the piston 23A at the top dead center position is provided so as to become gradually smaller as it becomes circumferentially farther from the largest portion.
  • the inclined surface (chamfer) of the convex corner portion 18b is provided within a quarter-peripheral region with a portion corresponding to the piston 23A at the top dead center position being in the middle.
  • the inclined surface (chamfer) is provided so that a portion corresponding to the piston 23B at the bottom dead center position is the largest, and gradually becomes smaller as the portion is circumferentially separated from the portion.
  • the inclined surface (chamfered) of the convex corner portion 18c is provided within a quarter-peripheral region with a portion corresponding to the piston 23B at the bottom dead center position as a center.
  • the inclined surface (chamfer) of the convex corner portion 18c is provided with substantially the same size as the inclined surface (chamfer) of the convex corner portion 18b in consideration of the weight balance around the center axis Ml of the first swash plate 18. Has been.
  • the present embodiment having the above configuration has the following effects.
  • the first shower 25A and the The thickness between 2 SHU and 25B becomes thicker.
  • the second swash plate 51 is eccentric with respect to the first swash plate 18 so that the second shroud 25B and the second swash plate 51 of the piston 23 near the top dead center position are connected to each other.
  • the contact area of the second swash plate 51 and the second shoe 25B can be improved while suppressing the decrease in the durability and the size of the piston 23. It is effective for
  • a convex corner portion 18c on the second swash plate 51 side protrudes largely in the radial direction of the drive shaft 16 at an outer peripheral edge corresponding to the piston 23B at the bottom dead center position. It will be.
  • Carbon dioxide is used as the refrigerant in the refrigeration circuit.
  • a carbon dioxide refrigerant When a carbon dioxide refrigerant is used, the pressure in the refrigeration circuit is much higher than when a chlorofluorocarbon refrigerant (for example, R134a) is used. Therefore, also in the compressor, the compression reaction force acting on the piston 23 increases, and the pressing force between the second swash plate 51 and the second shoe 25B increases.
  • embodying the present invention is particularly effective in improving the durability of the second swash plate 51 and the second shoe 25B while suppressing the decrease in the durability and the size of the piston 23. Becomes effective.
  • the first shoe 25A located on the hinge mechanism 19 side, that is, on the side opposite to the compression chamber 24, has a first sliding contact surface 25b opposite to the hemispheric surface 25a.
  • the swash plate 18 is slidably abutted against the front surface of the outer peripheral portion 18-1.
  • hinge machine The second shoe 25B on the side opposite to the structure 19, that is, on the compression chamber 24 side and receiving the compression reaction force has an outer peripheral portion 51-2 of the second swash plate 51 on a sliding contact surface 25b opposite to the hemispheric surface 25a. It is slidably abutted against the rear surface of the.
  • the sliding surface 25b of the first shoe 25A has a middle-high shape whose central portion protrudes toward the first swash plate 18 (see FIG. 4.
  • the middle-high shape is exaggerated in FIG. 4).
  • the sliding surface 25b of the second shoe 25B has a planar shape.
  • a radial bearing 52A composed of a rolling bearing is interposed between the support hole 51a and the inner peripheral surface of the support hole 51a.
  • the radial bearing 52A has an outer race 52a attached to the inner peripheral surface of the support hole 51a in the second swash plate 51, and an inner race 52b attached to the outer peripheral surface of the support portion 39 in the first swash plate 18.
  • a plurality of rollers 52c as rolling elements interposed between the outer race 52a and the inner race 52b.
  • a thrust made of a rolling bearing is provided between the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 51-2 of the second swash plate 51 between the first shoe 25A and the second shoe 25B.
  • Bearing 53 is interposed.
  • the thrust bearing 53 has a plurality of rollers 53a as rolling elements, and the plurality of rollers 53a are rotatably held by a retainer 53b.
  • an annular race 55 is interposed between the roller 53a and the first swash plate 18.
  • the race 55 is formed by subjecting a base material made of mild steel such as SPC to a carburizing heat treatment.
  • the corners at both ends of the roller 53a are chamfered to prevent the roller 53a from hitting the second swash plate 51 and the race 55 to damage the second swash plate 51 and the race 55. .
  • an annular locking portion 18 d protrudes from the outermost periphery of the outer peripheral portion 18-1 toward the second swash plate 51.
  • the race 55 is disposed inside the locking portion 18d, and the race 55 is locked to the first swash plate 18 on the radially outer side by abutment of the outer peripheral edge thereof with the locking portion 18d.
  • the race 55 is rotatable relative to the first swash plate 18 by being guided by the locking portion 18d.
  • the second swash plate 51 is supported by the first swash plate 18 via the radial bearing 52A and the thrust bearing 53 so that the second swash plate 51 can rotate relative to the first swash plate 18 and can be tilted integrally. Is held. Therefore, when the first swash plate 18 rotates, the radial bearing 52A and the thrust bearing 53 act to cause a rolling between the first swash plate 18 and the second swash plate 51, thereby causing the surfaces to face each other. Mechanical loss due to slippage is replaced by mechanical loss due to rolling, and the occurrence of mechanical loss in the compressor can be greatly suppressed.
  • the thickness Y1 of the inner peripheral portion 51-1 which is supported by the radial bearing 52A in the second swash plate 51, is the thickness Y2 of the outer peripheral portion 51-2, which is supported by the thrust bearing 53 in the second swash plate 51. It is thicker than it is.
  • the thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is at least half the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 18- of the first swash plate 18. It is set thinner than the thickness of 1.
  • the thickness Y1 of the inner peripheral portion 51-1 of the second swash plate 51 is larger than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18.
  • the inner peripheral portion 51-1 of the second swash plate 51 has a cylindrical first protruding portion 56 protruding from the first swash plate 18 side and a protruding portion on the opposite side to the first swash plate 18.
  • the second swash plate 51 has a greater thickness than the outer peripheral portion 51-2 of the second swash plate 51 by providing the cylindrical second projecting portion 57 (Y1> Y2).
  • the first protrusion 56 and the second protrusion 57 are disposed coaxially with the support hole 51a, and the inner peripheral surfaces of the first protrusion 56 and the second protrusion 57 are formed on the inner periphery of the support hole 51a. Form a part of the surface.
  • the outer diameter Z2 of the second protrusion 57 is smaller than the outer diameter Z1 of the first protrusion 56. Further, the outer peripheral angle 57a of the distal end surface of the second projecting portion 57 is chamfered in a tapered shape as a whole.
  • a second swash plate 18 is provided between the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 51-2 of the second swash plate 51.
  • a thrust bearing 53 that supports the plate 51 so as to be rotatable relative to the first swash plate 18 is provided.
  • the second swash plate 51 is rotated relative to the first swash plate 18 between the inner peripheral portion (support portion 39) of the first swash plate 18 and the inner peripheral portion 51-1 of the second swash plate 51.
  • a radial bearing 52A is provided for supporting as much as possible.
  • the force S can effectively reduce the rotational resistance generated between the inner peripheral portion (support portion 39) and the inner peripheral portion 51-1 of the second swash plate 51. Therefore, even in the compressor 10 used for the refrigeration circuit using carbon dioxide as a refrigerant, the slip between the first swash plate 18 and the second swash plate 51 can be a mechanical loss due to rolling. As a result, it is possible to effectively suppress problems such as mechanical loss and seizure. Wear.
  • the thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is equal to or more than half the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 and the thickness of the outer peripheral portion 18_1. It is thinner than thickness X.
  • the space between the first shoe 25 ⁇ and the second shoe 25 ⁇ will be limited. In this limited space, if the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 is increased, the thickness ⁇ 2 of the outer peripheral portion 51-2 of the second swash plate 51 must be reduced.
  • the thickness ⁇ 2 of the outer peripheral portion 51-2 of the swash plate 51 is increased, the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 needs to be reduced.
  • the first swash plate 18 and the second swash plate 51 both secure the strength by increasing the thicknesses X and ⁇ 2 of the outer peripheral portions 18-1, 51-2 as much as possible.
  • the thickness X of the outer peripheral portion 18-1 can be secured by sliding with respect to the first swash plate 18. The priority should be given to securing the thickness 51 of the outer peripheral portion 51-2 of the plate 51.
  • the force of the second swash plate 51 is set such that the thickness ⁇ 2 of the outer peripheral portion 51-2 is equal to or more than half the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 18-1 It is to be set thinner than the sheet thickness X of.
  • the plate thickness Y1 of the inner peripheral portion 51-1 is larger than the plate thickness ⁇ 2 of the outer peripheral portion 51-2.
  • the thick inner peripheral portion 51-1 stabilizes the support of the second swash plate 51 by the radial bearing 52 °, and can further improve the sliding between the first swash plate 18 and the second swash plate 51.
  • the outer peripheral portion 51-2 of the second swash plate 51 which is relatively thinner than the inner peripheral portion 51-1, allows the outer peripheral portion 18- of the first swash plate 18 to be stronger in strength than the second swash plate 51. (1) It is easy to secure the plate thickness.
  • the thickness ⁇ 2 of the outer peripheral portion 51-2 of the second swash plate 51 is smaller than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18. Therefore, the thin outer peripheral portion 51-2 of the second swash plate 51 facilitates securing the thickness of the outer peripheral portion 18-1 of the first swash plate 18, which is stricter in strength than the second swash plate 51.
  • the thickness Y1 of the inner peripheral portion 51-1 is larger than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18. Therefore, the support of the second swash plate 51 by the radial bearing 52 ° is further stabilized.
  • the outer diameter of the second projecting portion 57 ⁇ 2 Is smaller than the outer diameter Z1 of the first protrusion 56.
  • Part of the second protruding portion 57 comes extremely close to the piston 23B at the bottom dead center position, for example, in a state where the discharge capacity of the compressor 10 is maximum (the state in FIG. 3). Therefore, making the second projecting portion 57 smaller in diameter than the first projecting portion 56 and separating it from the piston 23 avoids the interference between the second swash plate 51 and the bistone 23 and reduces the second swash plate. This is effective in increasing the thickness Y1 of the inner peripheral portion 51-1 of the plate 51.
  • a chamfer is provided at an outer peripheral angle 57a of the tip end surface.
  • a part of the outer peripheral angle 57a of the distal end surface is extremely close to the piston 23B at the bottom dead center position. Therefore, providing a chamfer at the outer peripheral angle 57a of the distal end surface of the second projecting portion 57 avoids interference between the second swash plate 51 and the piston 23 and reduces the inner peripheral portion 51a of the second swash plate 51. This is effective in achieving a balance between increasing the thickness of Y1.
  • a portion of the outer peripheral edge of the first swash plate 18 corresponding to the piston 23A at the top dead center position has an inclined surface (a convex corner portion 18b opposite to the second swash plate 51). Chamfer). Therefore, the diameter of the first swash plate 18 and the second swash plate 51 can be increased while suppressing a decrease in durability and an increase in size of the piston 23. Accordingly, the contact slidability between the second swash plate 51 and the second shoe 25B is improved, and the durability of the second swash plate 51 and the second shoe 25B is reduced while suppressing the decrease in the durability and the size of the piston 23. Can be improved.
  • the first swash plate 18 inclined with respect to the drive shaft 16 has a convex corner 18b (chamfered) opposite to the second swash plate 51 at the outer peripheral edge corresponding to the piston 23A at the top dead center position.
  • a neck 38 of the piston 23 corresponding to the protruding portion is formed in order to avoid interference with the protruding portion. It is conceivable to reduce the wall thickness or increase the diameter of the neck 38 in the radial direction. However, reducing the thickness of the neck 38 reduces the durability of the piston 23, and increasing the size of the neck 38 leads to an increase in the size of the compressor.
  • the roller 52c is used as a rolling element of the radial bearing 52A.
  • a rolling bearing using the roller 52c as a rolling element has better load resistance than, for example, a case using a ball as a rolling element. This leads to a reduction in the size of the radial bearing 52A and a reduction in the size of the compressor 10.
  • the race 55 is interposed between the roller 53a of the thrust bearing 53 and the first swash plate 18.
  • the race 55 is rotatable relative to the first swash plate 18.
  • the race 55 is interposed between the roller 53a and the first swash plate 18, and the compression reaction force acting on the roller 53a reduces the surface pressure through the race 55. Then, since the first swash plate 18 acts on the first swash plate 18, it is possible to suppress the first swash plate 18 from being locally worn and deteriorated. Further, in the race 55 that rotates relative to the first swash plate 18, the portions where a large compression reaction force acts via the rollers 53a are sequentially switched, so that it is possible to prevent the race 55 from being locally worn and deteriorated.
  • a locking portion 18d protrudes from the outer peripheral portion 18-1 of the first swash plate 18 toward the second swash plate 51, and abuts against the locking portion 18d. As a result, the race 55 is locked to the first swash plate 18 on the radially outer side.
  • the first swash plate 18 When the lubricating oil (refrigerant oil) attached to the cylinder moves radially outward due to the action of centrifugal force, the lubricating oil enters between the first swash plate 18 and the race 55 at the locking portion. It will be hindered. According to the present embodiment in which the race 55 is locked to the first swash plate 18 on the radial outside, the lubricating oil enters between the first swash plate 18 and the race 55 by the locking portion 18d.
  • the lubricating oil refrigerant oil
  • the locking portion 18d has an annular shape. Accordingly, the locking of the race 55 by the locking portion 18d is performed stably, and the sliding between the race 55 and the first swash plate 18 is further improved.
  • the support portion 39 is not eccentric with respect to the center axis Ml of the first swash plate 18. That is, the second swash plate 51, the radial bearing 52A (see FIG. 3) and the thrust bearing 53 (including the race 55) are not eccentric with respect to the first swash plate 18.
  • a portion corresponding to the piston 23B at the bottom dead center position is such that the convex corner portion 18c on the second swash plate 51 side is radially larger than the second swash plate 51. Since it does not protrude, there is no problem if the chamfered portion 18c is not chamfered as shown in FIG.
  • the PCD force of the thrust bearing 53 is set at the center point of the first shoe 25A and the second shoe 25B about the central axis Ml, M2 of the first swash plate 18 and the second swash plate 51. It is made larger than the diameter of the virtual cylinder passing through P. In this way, the thrust bearing 53 (the roller 53a) can suitably receive the compression reaction force transmitted through the second swash plate 51, and the durability is improved.
  • the “PCD” of the thrust bearing 53 means that the center of the thrust bearing 53 (the center axes Ml and M2 of the first swash plate 18 and the second swash plate 51) is the center axis, and the roller 53a is on the rotation center axis. Refers to the diameter of the virtual cylinder passing through the intermediate point.
  • the drive shaft 16 has the rotor 17 fixed thereto, and the swash plate 58 supported so as to be slidable and tiltable in the axial direction of the drive shaft 16.
  • Connecting pieces 59 and 60 are fixed to the swash plate 58, and guide pins 61 and 62 are fixed to the connecting pieces 59 and 60.
  • the rotor 17 has a pair of guide holes 171 (only one is shown).
  • the heads of the guide pins 61 and 62 are slidably fitted into the guide holes 171.
  • the swash plate 58 can be tilted in the axial direction of the drive shaft 16 and rotates integrally with the drive shaft 16 by linking the guide hole 171 and the guide pins 61 and 62. It is possible.
  • the tilt of the swash plate 58 is guided by the slide guide relationship between the guide hole 171 and the guide pins 61 and 62 and the slide support action of the drive shaft 16.
  • the connecting pieces 59 and 60, the guide pins 61 and 62, and the guide hole 171 constitute a hinge mechanism 19A.
  • the solid line position of the swash plate 58 in Fig. 6 indicates the maximum inclination state of the swash plate 58.
  • the dashed line position of the swash plate 58 in FIG. 6 indicates the minimum inclination state of the swash plate 58.
  • a portion corresponding to the piston 23A at the top dead center position and a portion located in the front and rear direction with respect to the portion are provided with a convex corner portion 58a opposite to the piston 23.
  • an inclined surface is provided at the convex corner 58a opposite to the piston 23. ing. As shown in FIG. 7, the inclined surface of the convex corner portion 58a is provided so that the portion corresponding to the piston 23 at the top dead center position becomes gradually smaller as it is further away in the circumferential direction from the largest portion. Have been.
  • the inclined surface provided at the convex corner portion 58a is a virtual cylinder having a central axis M3 parallel to the axis L of the drive shaft 16. It is on the circumference of C.
  • the center axis M3 is shifted from the piston 23A at the top dead center position to the drive shaft 16 with respect to the axis L.
  • the diameter of the virtual cylinder C is equal to or larger than the diameter of the swash plate 58.
  • the swash plate 58 inclined with respect to the drive shaft 16 has a convex corner portion 58a opposite to the piston 23 at the outer peripheral edge corresponding to the piston 23A at the top dead center position. Will protrude greatly. Therefore, by providing an inclined surface at a protruding portion (a part of the convex corner portion 58a) of the swash plate 58, it is possible to increase the diameter of the swash plate 58 while suppressing a decrease in durability and an increase in size of the piston 23. . Therefore, a large compression reaction force acting on the swash plate 58 can be suitably received through the second shoe 25B of the piston 23 near the top dead center position. This leads to improved durability of the swash plate 58.
  • the radial bearing 52 and the thrust bearing 53 are omitted, and the second swash plate 51 is fixed to the first swash plate 18 so that the second swash plate 51 is connected to the first swash plate 18. Be able to rotate integrally.
  • a slope is formed at the convex corner on the first swash plate 18 side with respect to the portion corresponding to the piston 23A at the top dead center position.
  • a slope is provided at a convex corner opposite to the first swash plate 18 with respect to a portion corresponding to the piston 23B at the bottom dead center position.
  • the second swash plate 51 inclined with respect to the drive shaft 16 has a convex angle on the first swash plate 18 side at the outer peripheral edge corresponding to the piston 23A at the top dead center position.
  • the portion protrudes largely in the radial direction of the drive shaft 16.
  • the swash plate structure to which the present invention can be applied is not limited to the structure using only the first swash plate and the second swash plate. It may have a plurality of swash plates.
  • the present invention is applied to a variable displacement swash plate type compressor having a double-headed piston.
  • the second swash plate may be arranged only on one side of the front and rear surfaces of the first swash plate, or the second swash plate may be arranged on both sides of the front and rear surfaces of the first swash plate. Is also good.
  • the present invention is not limited to application to a refrigerant compressor used in a refrigeration circuit, but may be applied to, for example, an air compressor.
  • the second embodiment is changed, for example, as shown in FIG. 5, the sliding surface 25b of the first shoe 25A is made flat.
  • the second embodiment is changed, for example, as shown in Fig. 5, the sliding contact surface 25b of the second shoe 25B is formed in a concave shape with a concave central portion.
  • the weight of the second shoe 25B reciprocating linearly with the piston 23 can be reduced, the inertia force of the second shoe 25B can be reduced, and the first swash plate 18 and the second swash plate 51 can be reduced.
  • the change of the inclination angle that is, the change of the displacement of the compressor, can be performed smoothly.
  • the thrust bearing 53 is changed to a rolling bearing provided with balls as rolling elements.
  • the thrust bearing 53 is changed to a plain bearing.
  • the radial bearing 52A is configured to receive only a radial load (a load in a direction orthogonal to the center axis M2) acting on the second swash plate 51.
  • a radial load a load in a direction orthogonal to the center axis M2
  • the roller 52c By changing this, for example, by arranging the roller 52c so as to be inclined with respect to the center axis M2 of the second swash plate 51, not only the radial load but also the thrust load (in the direction along the center axis M2) can be adjusted. Load).
  • the thrust bearing 53 is configured to receive only the thrust load acting on the second swash plate 51.
  • the rollers 53a By changing this, for example, by arranging the rollers 53a so as to be inclined with respect to the board surface of the second swash plate 51, a configuration in which not only a thrust load but also a radial load can be received.
  • the locking portion 18d is omitted, and a locking portion is provided on the inner peripheral portion of the first swash plate 18 (for example, the base of the support portion 39 also serves as the locking portion).
  • the swash plate 55 is to be locked to the first swash plate 18 on the radial inside.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un compresseur à plateau oscillant à déplacement variable, dans lequel un premier plateau oscillant (18) est connecté à un arbre d'entraînement (16) afin de tourner ensemble, et des pistons à deux têtes (23) sont ancrés au premier plateau oscillant (18) par l'intermédiaire de patins (25A, 25B). Les pistons (23) effectuent un mouvement de va-et-vient linéaire par rotation du premier plateau oscillant (18) en fonction de la rotation de l'arbre d'entraînement (16) afin de comprimer un gaz réfrigérant. Un second plateau oscillant (51) annulaire est supporté, de manière relativement rotative l'un par rapport à l'autre, par le premier plateau oscillant (18) par l'intermédiaire d'un roulement à billes (52). Ce second plateau oscillant (51) est disposé entre le premier plateau oscillant (51) et les patins (25B) sur un côté recevant une charge compressive coulissant sur le premier plateau oscillant (18) et les patins (25B). Des faces inclinées (parties chanfreinées) sont formées sur des parties de coin (18b, 18c) en saillie du premier plateau oscillant (18). De ce fait, il est possible d'augmenter la durabilité des plateaux oscillants et des patins.
PCT/JP2004/011373 2003-09-02 2004-08-06 Compresseur a plateau oscillant a deplacement variable WO2005024233A1 (fr)

Priority Applications (3)

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US10/570,482 US20070081904A1 (en) 2003-09-02 2004-08-06 Variable displacement type compressor
JP2005513610A JPWO2005024233A1 (ja) 2003-09-02 2004-08-06 容量可変型斜板式圧縮機
EP04771372A EP1669600A1 (fr) 2003-09-02 2004-08-06 Compresseur a plateau oscillant a deplacement variable

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JP2003-310291 2003-09-02
JP2003310291 2003-09-02
JP2003326962 2003-09-18
JP2003-326962 2003-09-18

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Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2004015269A1 (ja) * 2002-08-07 2005-12-02 株式会社豊田自動織機 容量可変型圧縮機
JP2009062856A (ja) * 2007-09-05 2009-03-26 Toyota Industries Corp 斜板式圧縮機
DE102010021708A1 (de) * 2010-05-27 2011-12-01 Claas Selbstfahrende Erntemaschinen Gmbh Hydrostatische Maschine
US20140345449A1 (en) * 2013-05-23 2014-11-27 Gholamali Kyoumars Saham Variable displacement devices and related methods
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0676659U (ja) * 1993-04-08 1994-10-28 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
JP2003042065A (ja) * 2001-07-26 2003-02-13 Toyota Industries Corp ピストン式容量可変型流体機械

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3790942B2 (ja) * 1997-05-26 2006-06-28 株式会社ヴァレオサーマルシステムズ 斜板式圧縮機
JP2001336477A (ja) * 2000-05-24 2001-12-07 Sanden Corp 圧縮機
US6582200B2 (en) * 2000-07-14 2003-06-24 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate compressor having shoes made of a magnesium-based material
JP2002039062A (ja) * 2000-07-26 2002-02-06 Toyota Industries Corp 圧縮機
JP2002089437A (ja) * 2000-09-13 2002-03-27 Toyota Industries Corp 圧縮機における潤滑用皮膜形成対象部品
JP2002180964A (ja) * 2000-12-12 2002-06-26 Toyota Industries Corp 圧縮機の摺動部品及び圧縮機
JP2002257042A (ja) * 2001-02-28 2002-09-11 Toyota Industries Corp 圧縮機における潤滑面形成対象部品
JP4496662B2 (ja) * 2001-04-20 2010-07-07 株式会社豊田自動織機 斜板式圧縮機における斜板
JP3890966B2 (ja) * 2001-12-06 2007-03-07 株式会社豊田自動織機 固定容量型ピストン式圧縮機における潤滑構造
US6705841B2 (en) * 2002-03-01 2004-03-16 Visteon Global Technologies, Inc. Variable displacement compressor with stepped shaft
DE10318626A1 (de) * 2002-04-25 2003-11-13 Sanden Corp Kompressor variabler Kapazität
JP4130566B2 (ja) * 2002-09-25 2008-08-06 株式会社テージーケー 可変容量圧縮機用容量制御弁
JP2004251256A (ja) * 2003-02-21 2004-09-09 Sanden Corp 斜板式圧縮機
JP4107141B2 (ja) * 2003-02-21 2008-06-25 株式会社デンソー リミッタ装置
JP4025832B2 (ja) * 2003-04-14 2007-12-26 株式会社豊田自動織機 圧縮機
JP2005188406A (ja) * 2003-12-25 2005-07-14 Toyota Industries Corp 斜板式圧縮機
JP4062265B2 (ja) * 2004-02-24 2008-03-19 株式会社豊田自動織機 可変容量圧縮機
JP2006291881A (ja) * 2005-04-13 2006-10-26 Toyota Industries Corp 斜板式圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0676659U (ja) * 1993-04-08 1994-10-28 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
JP2003042065A (ja) * 2001-07-26 2003-02-13 Toyota Industries Corp ピストン式容量可変型流体機械

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US20070081904A1 (en) 2007-04-12
KR20060057626A (ko) 2006-05-26
EP1669600A1 (fr) 2006-06-14

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