Deprecated: The each() function is deprecated. This message will be suppressed on further calls in /home/zhenxiangba/zhenxiangba.com/public_html/phproxy-improved-master/index.php on line 456
EP1669600A1 - Compresseur a plateau oscillant a deplacement variable - Google Patents
[go: Go Back, main page]

EP1669600A1 - Compresseur a plateau oscillant a deplacement variable - Google Patents

Compresseur a plateau oscillant a deplacement variable Download PDF

Info

Publication number
EP1669600A1
EP1669600A1 EP04771372A EP04771372A EP1669600A1 EP 1669600 A1 EP1669600 A1 EP 1669600A1 EP 04771372 A EP04771372 A EP 04771372A EP 04771372 A EP04771372 A EP 04771372A EP 1669600 A1 EP1669600 A1 EP 1669600A1
Authority
EP
European Patent Office
Prior art keywords
swash plate
outer circumferential
piston
drive shaft
shoes
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.)
Withdrawn
Application number
EP04771372A
Other languages
German (de)
English (en)
Inventor
H. Kabushiki Kaisha Toyota Jidoshokki KURITA
T. Kabushiki Kaisha Toyota Jidoshokki IMAI
M. Kabushiki Kaisha Toyota Jidoshokki Murase
T. Kabushiki Kaisha Toyota Jidoshokki FUKANUMA
M. Kabushiki Kaisha Toyota Jidoshokki OTA
F. Kabushiki Kaisha Toyota Jidoshokki 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
Publication of EP1669600A1 publication Critical patent/EP1669600A1/fr
Withdrawn legal-status Critical Current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 93A, 93B. 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 93A, 93B causing the pistons 94 to reciprocate, thereby compressing refrigerant gas.
  • Each pair of shoes 93A, 93B 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 93A, 93B rotate relative to the swash plate 92.
  • the rotation of the shoes 93A, 93B about the axis S is caused because a rotational force is applied to the shoes 93A, 93B 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 93A, 93B directly slide against the swash plate 92. Therefore, the shoes 93A, 93B are unnecessarily rotated about the axis S due to the sliding motion caused as the shoes 93A, 93B 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 93B that receives reactive force of compression, and causes problems such as seizure at the sliding portions.
  • an annular step 90a 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 90a 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 93B to be slidable with respect to the first swash plate 90 and the second shoes 93B.
  • 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 93B about the axis S caused by the relative rotation of the second swash plate 95 and the second shoes 93B 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 93A and the second shoes 93B 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 93B 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 93B as compared to the relative rotation speed of the second shoes 93B and the first swash plate 90.
  • the first swash plate 90 which tilts with respect to the drive shaft 91, has a salient corner 90b 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 90b 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 95b 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 95b 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.
  • 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.
  • variable displacement swash plate type compressor forms part of a refrigeration circuit of a vehicle air-conditioning system.
  • 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, and 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 18a is formed at the center of the first swash plate 18.
  • the drive shaft 16 is inserted through the through hole 18a of the first swash plate 18.
  • the first swash plate 18 is supported by the drive shaft 16 via the through hole 18a 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 51a is formed at the center of the second swash plate 51. The support portion 39 is inserted in the support hole 51a.
  • 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 51a 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 53a in this embodiment, and the rollers 53a are rotatably held by a retainer 53b.
  • 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 43a 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 43a 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 43a 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 38a are formed in each neck 38.
  • Each neck 38 accommodates semispherical first and second shoes 25A, 25B.
  • the first shoe 25A and the second shoe 25B 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 25A and the second shoe 25B are each received by the corresponding shoe seat 38a via a semispherical surface 25a.
  • the semispherical surface 25a of the first shoe 25A and the semispherical surface 25a of the second shoe 25B 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 25A and the second shoe 25B.
  • the first shoe 25A located opposite to the compression chamber 24 abuts against the front surface of the first swash plate 18 via a planar sliding surface 25b provided opposite to the semispherical surface 25a.
  • the second shoe 25B 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 25b provided opposite to the semispherical surface 25a.
  • 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 M1 of the first swash plate 18 toward the piston 23A 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 M1.
  • 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 23A located at the top dead center position. Therefore, the axis M2 of the second swash plate 51, the radial bearing 52, and the thrust bearing 53 is slightly displaced in parallel from the axis M1 of the first swash plate 18 toward the center point P of the first shoe 25A and the second shoe 25B of the piston 23A 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 23A 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 25B 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 23B 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. 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 25B of the piston 23 located in the vicinity of the bottom dead center position and the second swash plate 51 is reduced.
  • reaction force of compression applied to the second shoe 25B 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 25B of the piston 23 located in the vicinity of the top dead center position. Therefore, even if the contact area between the second shoe 25B 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 25B.
  • Part of the outer circumferential edge portion of the first swash plate 18 corresponding to the piston 23A located at the top dead center position and circumferentially adjacent parts thereof are provided with an inclined surface (a chamfer) on a salient corner 18b 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 18b 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 18b opposite to the piston 23A.
  • the inclined surface (the chamfer) on the salient corner 18b is the largest at the part corresponding to the piston 23A located at the top dead center position, and gradually becomes smaller along the circumferential direction.
  • the inclined surface (the chamfer) on the salient corner 18b is provided within a range of quarter to half the circumference of the first swash plate 18 with the part corresponding to the piston 23A 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 23B located at the bottom dead center position and circumferentially adjacent parts thereof are provided with an inclined surface (a chamfer) on a salient corner 18c 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 23B at the bottom dead center position is provided with the inclined surface on the salient corner 18c opposite to the piston 23B.
  • the inclined surface (the chamfer) is the largest at the part corresponding to the piston 23B located at the bottom dead center position, and gradually becomes smaller along the circumferential direction.
  • the inclined surface (the chamfer) of the salient corner 18c is provided within a range of quarter to half the circumference of the first swash plate 18 with the part corresponding to the piston 23B located at the bottom dead center position arranged in the middle.
  • the inclined surface (the chamfer) on the salient corner 18c is substantially the same size as the inclined surface (the chamfer) on the salient corner 18b taking into consideration of the balance of the weight around the axis M1 of the first swash plate 18.
  • the first embodiment has the following advantages.
  • 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 25B 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.
  • the center portion of the sliding surface 25b of the first shoe 25A bulges toward the first swash plate 18 (see Fig. 4. The bulge is exaggerated in Fig. 4).
  • the sliding surface 25b of the second shoe 25B is flat.
  • a radial bearing 52A 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 51a of the second swash plate 51.
  • the radial bearing 52A includes an outer race 52a attached to the inner circumferential surface of the support hole 51a of the second swash plate 51, an inner race 52b attached to the outer circumferential surface of the support portion 39 of the first swash plate 18, and rolling elements, which are rollers 52c in the second embodiment.
  • the rollers 52c are located between the outer race 52a and the inner race 52b.
  • the thrust bearing 53 which is a roller bearing, is located between the first shoes 25A and the second shoes 25B 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 53a in the second embodiment, and the rollers 53a are rotatably held by the retainer 53b.
  • the thrust bearing 53 has an annular race 55 located between the rollers 53a 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 53a are chamfered to prevent the second swash plate 51 and the race 55 from being damaged by the rollers 53a abutting against the second swash plate 51 and the race 55.
  • An annular engaging portion 18d 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 18d 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 18d.
  • the race 55 is guided by the engaging portion 18d 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 52A 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 52A 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 Y1 of the inner circumferential portion 51-1 of the second swash plate 51 that is supported by the radial bearing 52A is greater than the plate thickness Y2 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 Y2 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 Y1 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 (Y1 > Y2) 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 51a, 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 51a.
  • the outer diameter Z2 of the second projection 57 is smaller than the outer diameter Z1 of the first projection 56.
  • the outer circumferential corner 57a 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 support portion 39 is not decentered from the axis M1 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 decentered from the first swash plate 18.
  • the salient corner 18c need not be chamfered as shown in Fig. 5 because the salient corner 18c 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 M1, M2 of the first swash plate 18 and the second swash plate 51 and passes through the center points P of the first shoe 25A and the second shoe 25B.
  • the thrust bearing 53 (the rollers 53a) 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 M1, M2 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 53a.
  • 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, and 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 19A.
  • 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 23A located at the top dead center position and circumferentially adjacent parts thereof are provided with an inclined surface on a salient corner 58a 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 19A is provided with the inclined surface on the salient corner 58a toward the hinge mechanism 19A. 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 23A at the top dead center position is provided with the inclined surface on the salient corner 58a opposite to the piston 23. As shown in Fig. 7, part of the inclined surface of the salient corner 58a 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 58a is located on the circumferential surface of an imaginary cylinder C having an axis M3 that is parallel to the axis L of the drive shaft 16.
  • the axis M3 is displaced with respect to the axis L from the piston 23A 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 58a 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 58a) 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 25B of the piston 23 located in the vicinity of the top dead center position. This improves the durability of the swash plate 58.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP04771372A 2003-09-02 2004-08-06 Compresseur a plateau oscillant a deplacement variable Withdrawn EP1669600A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2003310291 2003-09-02
JP2003326962 2003-09-18
PCT/JP2004/011373 WO2005024233A1 (fr) 2003-09-02 2004-08-06 Compresseur a plateau oscillant a deplacement variable

Publications (1)

Publication Number Publication Date
EP1669600A1 true EP1669600A1 (fr) 2006-06-14

Family

ID=34277688

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04771372A Withdrawn EP1669600A1 (fr) 2003-09-02 2004-08-06 Compresseur a plateau oscillant a deplacement variable

Country Status (5)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2034182A3 (fr) * 2007-09-05 2009-11-25 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau en biais

Families Citing this family (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
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
CN109863301A (zh) 2016-07-25 2019-06-07 开罗股份有限公司 摇摆板式压缩机和使用它的氧气浓缩器

Family Cites Families (22)

* 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
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
JP2003003954A (ja) * 2001-06-21 2003-01-08 Sanden Corp 斜板式圧縮機
JP4934921B2 (ja) * 2001-07-26 2012-05-23 株式会社豊田自動織機 ピストン式容量可変型流体機械
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
US6939112B2 (en) * 2002-04-25 2005-09-06 Sanden Corporation Variable displacement compressors
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
JP4107141B2 (ja) * 2003-02-21 2008-06-25 株式会社デンソー リミッタ装置
JP2004251256A (ja) * 2003-02-21 2004-09-09 Sanden Corp 斜板式圧縮機
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005024233A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2034182A3 (fr) * 2007-09-05 2009-11-25 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau en biais

Also Published As

Publication number Publication date
US20070081904A1 (en) 2007-04-12
WO2005024233A1 (fr) 2005-03-17
KR20060057626A (ko) 2006-05-26
JPWO2005024233A1 (ja) 2006-11-02

Similar Documents

Publication Publication Date Title
US9228573B2 (en) Wabble plate type variable displacement compressor
US8327751B2 (en) Wabble plate type variable displacement compressor
EP1533533A1 (fr) Roulement a deux rangees de billes concu pour soutenir une poulie
US5556261A (en) Piston type compressor
EP1669600A1 (fr) Compresseur a plateau oscillant a deplacement variable
US9046089B2 (en) Wobble plate type variable displacement compressor
US7455008B2 (en) Swash plate compressor
JP2005113907A (ja) 斜板式圧縮機
EP1092872A2 (fr) Piston pour compresseur à plateau en biais
US20110088547A1 (en) Wobble Plate-Type Variable Displacement Compressor
EP0856663A2 (fr) Compresseur à plateau en biais à capacité variable
EP1087136B1 (fr) Tête de piston de compresseur à plateau en biais avec chanfrein
EP2309127A1 (fr) Compresseur à déplacement variable du type à plateau oscillant
CN100422553C (zh) 斜盘式压缩机
KR100748140B1 (ko) 가변용량 사판식 압축기의 구동축 지지용 스러스트 베어링지지구조
JP4314405B2 (ja) 可変容量型斜板式圧縮機
US20180051682A1 (en) Wobble Plate Type Variable Displacement Compressor
EP1288496A2 (fr) Compresseur à capacité variable
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
JP2005351101A (ja) 斜板式コンプレッサ
JP2006009626A (ja) 可変容量圧縮機
JP2003328931A (ja) 揺動斜板式圧縮機

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20060307

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR IT

R17P Request for examination filed (corrected)

Effective date: 20060302

RBV Designated contracting states (corrected)

Designated state(s): DE FR IT

RIN1 Information on inventor provided before grant (corrected)

Inventor name: IMAI, TAKAYUKIKABUSHIKI KAISHA TOYOTA JIDOSHOKKI

Inventor name: KURITA, HAJIMEKABUSHIKI KAISHA TOYOTA JIDOSHOKKI

Inventor name: FUKANUMA, TETSUHIKOK. K. TOYOTA JIDOSHOKKI

Inventor name: MURASE, MASAKAZUK. K. TOYOTA JIDOSHOKKI

Inventor name: OTA, MASAKIK. K.TOYOTA JIDOSHOKKI

Inventor name: ENOKIJIMA, FUMINOBUK. K. TOYOTA JIDOSHOKKI

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR IT

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

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20071128