WO2007049523A1 - Compresseur a cylindree variable - Google Patents

Compresseur a cylindree variable Download PDF

Info

Publication number
WO2007049523A1
WO2007049523A1 PCT/JP2006/320963 JP2006320963W WO2007049523A1 WO 2007049523 A1 WO2007049523 A1 WO 2007049523A1 JP 2006320963 W JP2006320963 W JP 2006320963W WO 2007049523 A1 WO2007049523 A1 WO 2007049523A1
Authority
WO
WIPO (PCT)
Prior art keywords
sleeve
tilting
swash plate
link
drive shaft
Prior art date
Application number
PCT/JP2006/320963
Other languages
English (en)
Japanese (ja)
Inventor
Toshikatsu Miyaji
Ryuichi Hirose
Naoki Ishikawa
Satoshi Kubo
Original Assignee
Calsonic Kansei Corporation
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 Calsonic Kansei Corporation filed Critical Calsonic Kansei Corporation
Priority to EP06812092A priority Critical patent/EP1942275A4/fr
Priority to US12/091,662 priority patent/US20090246050A1/en
Publication of WO2007049523A1 publication Critical patent/WO2007049523A1/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
    • F04B27/1072—Pivot mechanisms
    • 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
    • F04B27/0895—Component parts, e.g. sealings; Manufacturing or assembly thereof driving 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
    • F04B27/14—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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber

Definitions

  • the present invention relates to a variable capacity compressor.
  • a conventional variable capacity compressor includes a drive shaft, a rotor fixed to the drive shaft and rotating integrally with the drive shaft, a sleeve mounted on the drive shaft so as to be slidable in the axial direction, and a sleeve
  • a swash plate that can be freely tilted a link mechanism that is interposed between the rotor and the swash plate and transmits the rotation of the rotor to the swash plate, and a piston that reciprocates as the swash plate rotates.
  • the link mechanism connects the rotor and the swash plate so that the rotation angle of the swash plate can be changed while transmitting the rotation of the rotor to the swash plate. Changing the tilt angle of the swash plate changes the piston stroke.
  • FIG. 9 shows a link mechanism corresponding to Japanese Patent Laid-Open No. 10-176658.
  • the link mechanism in FIG. 9 includes a pair of opposed rotor arms 145 and 146 projecting from the rotor 140 toward the swash plate 141, and a single projecting projecting from the swash plate 141 toward the rotor 140.
  • a swash plate arm 147 and a pair of link arms 142A and 142B are provided. These five arms 145, 142A, 147, 143B, 146 are stacked in the direction of torque transmission, whereby the rotation of the rotor 140 is transmitted to the swash plate.
  • each of the pair of link arms 142A and 142B is rotatably connected to the pair of rotor arms 145 and 146 by the first connecting pin 143, and the other end is connected to the swash plate arm 147 by the second connection.
  • Pins 144 are rotatably connected.
  • the link arms 142A and 142B rotate with respect to the rotor arms 145 and 146 around the connecting pin 143
  • the swash plate arm 147 rotates with respect to the link arms 142A and 142B around the connecting pin 144.
  • the inclination angle of the swash plate 141 can be changed with respect to the drive shaft (not shown).
  • the rotor arm 145 and the link arm 142A serve as a rotational torque transmission surface and a rotational sliding contact surface. That is, the contact surface between the rotor arm 145 and the link arm 142A is in sliding contact with the connecting pin 143 as a center while receiving a surface pressure due to a large rotational torque Ft. Further, the contact surface between the link arm 142A and the swash plate arm 147 rotates and slides relative to the connection pin 144 while receiving a surface pressure due to a large rotational torque Ft.
  • the swash plate 141 When the compressor is in operation (when the drive shaft is rotating), the swash plate 141 receives a compression reaction force Fp as much as a piston force connected to the swash plate 141.
  • This compression reaction force Fp may be shifted forward in the rotational direction of the link mechanism as shown in Fig. 9 (see Fig. 2).
  • a twisting load is applied to the swash plate arm 147 in the Y direction in the figure, and the swash plate 141 and the link 142 are bitten and twisted at two points (C, C), further increasing the sliding resistance. End up.
  • Patent Document 1 that solves such a problem, a force in which a washer is interposed between the contact surfaces of the rotor arm and the link arm and between the contact surfaces of the link arm and the swash plate arm. Even with such a structure, the same problem occurs.
  • the present invention has been made paying attention to the problems of the prior art, and an object thereof is to provide a variable capacity compressor capable of reducing a torsional load applied to a link mechanism.
  • One aspect of the present invention is a variable capacity compressor, a rotating member fixed to a drive shaft and rotating integrally therewith, and a three-piece mounted on the drive shaft so as to be slidable in the axial direction.
  • a tilting member rotatably mounted on the sleeve by a pivot pin, and connecting the rotating member and the tilting member to allow tilting of the tilting member while allowing the rotating member to rotate torque of the rotating member.
  • a tilting guide formed on a surface orthogonal to the pivot pin on each of the sleeve and the tilting member and in sliding contact with each other. A surface.
  • FIG. 1 is a cross-sectional view of a variable capacity compressor according to an embodiment of the present invention.
  • FIG. 2 is a perspective view of an assembly in which a swash plate and a rotor are assembled to a drive shaft.
  • FIG. 3 is an exploded perspective view of the assembly.
  • FIG. 4 is a sectional view of the assembly.
  • FIG. 5 (a) is a cross-sectional view taken along the line Va—Va in FIG. 4, and FIG. 5 (b) is a cross-sectional view taken along the line Vb—Vb in FIG.
  • FIG. 6 is a perspective view including a partially broken portion in a state where a sleeve is assembled to a swash plate hub.
  • FIG. 7 is a view showing a state in which a sleeve is assembled to a swash plate hub.
  • FIG. 7 (a) is a front view
  • FIG. 7 (b) is a side view
  • Fig. 8 is a cross-sectional view taken along line VIII-VIII in Fig. 7 (c), and Fig. 8 (a) is a view of the swash plate hub parallel to the sleeve. (b) is a view of the swash plate hub tilted with respect to the sleeve.
  • FIG. 9 is a sectional view showing an example of a link mechanism of a conventional variable capacity compressor.
  • variable capacity compressor according to an embodiment of the present invention will be described with reference to the drawings.
  • FIG. 1 is a cross-sectional view of a variable capacity compressor.
  • variable capacity compressor 1 of the present embodiment is a swash plate type variable capacity compressor.
  • the variable capacity compressor 1 includes a cylinder block 2 having a plurality of cylinder bores 3 (see FIG. 2) arranged at equal intervals in the circumferential direction, and a cylinder block 2 joined to the front end surface of the cylinder block 2 and cranked inside.
  • a front housing 4 that forms a chamber 5 and a rear housing 6 that is joined to a rear end surface of the cylinder block 2 via a valve plate 9 and that forms a suction chamber 7 and a discharge chamber 8 therein.
  • the cylinder block 2, the front housing 4 and the rear housing 6 are fastened and fixed by a plurality of through bolts 13 to constitute a compressor housing.
  • the valve plate 9 is formed with a suction hole 11 that communicates the cylinder bore 3 and the suction chamber 7, and a discharge hole 12 that communicates the cylinder bore 3 and the discharge chamber 8.
  • a suction valve mechanism (not shown) that opens and closes the suction hole 11 is provided on the surface of the valve plate 9 on the cylinder block 2 side. Discharge on the rear housing 6 side of the valve plate 9 A discharge valve mechanism (not shown) for opening and closing the hole 12 is provided. A gasket (not shown) is interposed between the valve plate 9 and the rear housing 6 so that the airtightness of the suction chamber 7 and the discharge chamber 8 is maintained.
  • the central through hole 14 as a bearing hole at the center of the cylinder block 2 and the front housing 4 is supported by a drive shaft 10 via radial bearings 15 and 19, thereby driving shaft 10 force S crank It is freely rotatable in chamber 5.
  • a thrust bearing 20 is interposed between the front end surface of a rotor 21 (described later) fixed to the drive shaft 10 and the inner wall surface of the rear housing 6, and the rear end of the central through hole 14 of the cylinder block 2.
  • a thrust bearing 16 is interposed between the adjusting screw 17 as a fixing member fixed to the side and the rear end surface of the drive shaft 10.
  • the crank chamber 5 includes a rotor 21 as a rotating member fixed to the drive shaft 10, a sleeve 22 slidably mounted on the drive shaft 10 in the axial direction, and a pivot pin 61 on the sleeve 22. And a swash plate 24 as a tilting member that can be pivoted with respect to the sleeve 22. That is, the swash plate 24 is attached to the drive shaft 10 via the sleeve 22 and the pivot pin 61, so that it can tilt with respect to the drive shaft 10 and slide in the axial direction of the drive shaft 10. .
  • the swash plate 24 includes a knob 25 attached to the sleeve 22 so as to be tiltable, and a swash plate body 26 fixed to a boss portion 25a of the hub 25.
  • a piston 29 is slidably accommodated in each cylinder bore 3, and this piston 29 is connected to a swash plate 24 via a pair of hemispherical piston shoes 30, 30.
  • a link mechanism 40 is interposed between the rotor 21 as the rotating member and the swash plate 24 as the tilting member.
  • the link mechanism 40 allows the rotational torque of the rotor 21 to be transmitted to the swash plate 24 while allowing the tilt angle of the swash plate 24 to be changed.
  • the inclination angle of the swash plate 24 decreases as the sleeve 22 moves closer to the cylinder block 2 side against the return spring 52, while the inclination angle of the swash plate 24 decreases, while the sleeve 22 resists the return spring 51. Then, when it moves away from the cylinder block 2, the inclination angle of the swash plate 24 increases.
  • Reference numeral 53 in FIG. 1 is a return spring stopper (for example, a C ring) that is locked in an annular groove formed in the drive shaft 10 and that compresses and holds the return spring 52 between the sleeve 22 and the like. is there.
  • This variable capacity compressor is provided with a pressure control mechanism.
  • the pressure control mechanism changes the tilt angle of the swash plate 24 by adjusting the differential pressure (pressure balance) between the crank chamber pressure Pc on the rear side of the piston 29 and the suction chamber pressure Ps on the front side of the piston 29. Change the piston stroke. When the piston stroke changes, the refrigerant discharge capacity of the compressor changes.
  • the pressure control mechanism includes an extraction passage (not shown) that connects the crank chamber 5 and the suction chamber 7, and an air supply passage (not shown) that connects the crank chamber 5 and the discharge chamber 8. And a control valve 33 provided in the middle of the air supply passage for controlling the opening and closing of the air supply passage.
  • FIG. 2 is a perspective view of an assembly in which a swash plate and a rotor are assembled to a drive shaft
  • FIG. 3 is an exploded perspective view of the assembly
  • FIG. 4 is a sectional view of the assembly
  • FIG. 5 (a) is in FIG. Fig. 5 (b) is a cross-sectional view taken along the line Vb-Vb in Fig. 4
  • Fig. 6 is a swash plate hub.
  • 7 is a perspective view including a partially broken portion in a state where a sleeve is assembled
  • FIG. 7 is a diagram showing a state where a sleeve is assembled to a hub of a swash plate
  • (a) is a front view
  • (b) is a side view.
  • Yes (c) is a cross-sectional view taken along line VIIc-VIIc in (b)
  • FIG. 8 is a cross-sectional view taken along line VIII-VIII in FIG. 7 (c)
  • FIG. FIG. 8 (b) is a diagram showing a state in which the swash plate hub is parallel
  • FIG. 8 (b) is a diagram showing a state in which the swash plate hub is inclined with respect to the sleeve.
  • the width dl of the slit 41s of the rotor 21 (that is, the width between the inner surfaces 41d and 41d of the pair of arms 41 and 41 of the rotor 21) and the width d2 of the slit 43s of the swash plate 24 (that is, the width of the swash plate 24)
  • a pair of arms 43 and 43 are formed to have the same width between the inner flanges J surface 43d and 43d), and the width dO of the link member 45 (that is, both of the link members 45) with respect to the widths dl and d2.
  • the width between the outer side surfaces 45e and 45e) is also formed to be substantially the same width, whereby the link member 45 is slidably fitted in both the slits 41s and 43s, and is always in sliding contact.
  • One end 45a of the link member 45 is rotatably connected to the pair of arms 41, 41 of the rotor 21 by a first connecting pin 46.
  • the other end 45 b of the link member 45 is rotatably connected to the pair of arms 43, 43 of the swash plate 24 by the second connecting pin 47.
  • a pair of arms 41, 41 of the rotor 21 is provided with a bearing hole 41a that rotatably supports the first connecting pin 46, and the first end 45a of the link member 45 has a first hole 45a.
  • a fixing hole 45c for fixing the connecting pin 46 by press-fitting is provided.
  • the pair of arms 43, 43 of the swash plate 24 is provided with a bearing hole 43a for rotatably supporting the second connecting pin 47, and the link portion
  • the other end 45b of the material 45 is provided with a fixing hole 45d for fixing the second connecting pin 47 by press fitting.
  • the first connecting pin 46 and the second connecting pin 47 have the same diameter and the same length.
  • the hub 25 is pivotally attached to the sleeve 22 by a pivot pin 61 that extends in a direction orthogonal to the drive shaft 10, and pivots while being guided by tilting guide surfaces 22 c and 25 e orthogonal to the pivot pin 61. It ’s like that.
  • the sleeve 22 is formed in a substantially cylindrical shape, and is attached to the drive shaft 10 so as to be slidable in the axial direction.
  • fixing holes 22b and 22b are formed concentrically on both sides of the drive shaft 10.
  • the fixing holes 22b and 22b extend in a direction perpendicular to the drive shaft 10, and the pivot pin 61 is fixed to the fixing holes 22b and 22b.
  • the swash plate hub 25 has bearing holes 25d and 25d formed concentrically on both sides of the drive shaft 10.
  • the bearing holes 25d and 25d extend in a direction orthogonal to the drive shaft 10.
  • the pivot pin 61 is inserted into the bearing holes 25d and 25d of the hub 25 with the sleeve 22 attached to the central port 25c of the hub 25, so that the pivot pin as shown in FIGS. 8 (a) and (b).
  • the hub 25 tilts with respect to the sleeve 22 around 61.
  • the sleeve 22 and the hub 25 are provided with tilting guide surfaces 22c and 25e that are in sliding contact with each other as shown in FIGS.
  • the tilt guide surfaces 22c and 25e are provided on both sides of the drive shaft 10 as surfaces orthogonal to the pivot pin 61. Therefore, the hub 25 is tilted about the pivot pin 61 with respect to the sleeve 22 while being guided by the tilt guide surfaces 22c and 25e.
  • the rotor 21 rotates integrally with the drive shaft 10.
  • the rotation of the rotor 21 is transmitted to the swash plate 24 via the link mechanism 40.
  • the rotation of the swash plate 24 is converted into a reciprocating motion of the piston 29 through a pair of pistons 30, 30, and the piston 29 reciprocates in the cylinder bore 3.
  • the reciprocating motion of the piston 29 causes the refrigerant valve plate in the suction chamber 7 to move. After being sucked into the cylinder bore 3 through the suction hole 11 of the cylinder 9, it is compressed in the cylinder bore 3, and is discharged into the discharge chamber 8 through the discharge hole 12 of the compressed refrigerant cover valve plate 9.
  • the pressure in the crank chamber 5 is adjusted by opening and closing the control valve 33, the pressure balance before and after the piston is adjusted, and the piston stroke is changed.
  • a compression reaction force Fp from the piston 29 is applied to the swash plate 24.
  • the compression reaction force Fp may be shifted forward in the rotational direction from the top dead center TDC of the swash plate 24 (position where the link mechanism 40 is located) depending on the rotational speed of the drive shaft 10. This is because the compression reaction force becomes maximum before the top dead center of the end of the compression stroke in the compression stroke of the piston 29.
  • the compression reaction force Fp is biased to the swash plate 24 forward in the rotational direction from the top dead center TDC, and a torsional load is applied to the swash plate 24.
  • the torsional load is received by the link mechanism 40 and the tilt guide surfaces 22c and 25e. For this reason, the torsional load applied to the link mechanism 40 that transmits the rotational torque and rotates and slides is reduced. As a result, the sliding resistance in the link mechanism 40 is reduced. That is, the sliding resistance between the link member 45 and the arms 41 and 43 decreases. More specifically, the sliding resistance between the outer side surface 45e of the link member and the inner side surface 41d of the arm 41 and the sliding resistance between the outer side surface 45e of the link member and the inner side surface 43d of the arm 43 are reduced). Thereby, the controllability of the compressor is improved. In the compressor 1 of the present embodiment, as shown in FIG.
  • the pair of tilting guide surfaces 22c, 22c of the sleeve 22 has a width d4 force.
  • the width 45 of the other end 45b of the material 45 is set wider. Therefore, more torsional loads can be received by the tilt guide surfaces 22c and 22c than the link mechanism 40, and the controllability of the compressor is further improved.
  • This embodiment is a variable capacity compressor, which is fixed to the drive shaft 10 and rotates integrally with the drive shaft 10, and is slidably mounted on the drive shaft 10 in the axial direction.
  • the rotation of the rotating member 21 while allowing the tilting member 24 to tilt by connecting the sleeve 22, the tilting member 24 rotatably mounted on the sleeve 22 by the pivot pin 61, and the rotating member 21 and the tilting member 24.
  • a link mechanism 40 for transmitting torque to the tilting member 24, and the tilting guide surfaces 22c and 25d formed on the sleeve 22 and the tilting member 24 as surfaces orthogonal to the pivot pin 61 are slidably contacted with each other.
  • This is a variable capacity compressor provided.
  • the link mechanism 40 includes the arm 41 projecting from the rotating member 21 toward the tilting member 24 and the arm 41 projecting from the tilting member 24 toward the rotating member 21. And the arm 43 of the rotating member and the arm 43 rotatably connected by a connecting pin (in this example, the first connecting pin 46 and the second connecting pin 47) directly or indirectly. Therefore, when changing the inclination angle of the tilting member 24, each member rotates around the pivot pin 61 of the sleeve 22 and the connecting pin of the link mechanism 40 (in this example, the connecting pins 46 and 47). Therefore, the friction form is “rolling-sliding friction”, so that the friction coefficient becomes extremely small, and the controllability of the compressor is further improved.
  • a connecting pin in this example, the first connecting pin 46 and the second connecting pin 47
  • the link mechanism 40 includes the pair of opposed arms 41, 41 projecting from the rotating member 21 toward the tilting member 24, and the tilting member 24 to the rotating member 21.
  • Towards A pair of opposed arms 43, 43 projecting from one end 45a is slidably fitted between a pair of arms 41, 41 of the rotating member, and the other end 45b is a pair of tilting members.
  • Link member 45 slidably fitted between the arms 43 and 43, and a first connecting pin 46 for rotatably connecting one end portion 45a of the link member and the arms 41 and 41 of the rotating member.
  • a second connecting pin 47 that rotatably connects the other end portion 45b of the link member and the arms 43, 43 of the tilting member.
  • each member rotates around the pivot pin 61 of the sleeve 22 and the connecting pins 46 and 47 of the link mechanism 40, so that the friction form is “Rolling sliding friction” makes the coefficient of friction extremely small and further improves the controllability of the compressor.
  • a pair of tilt guide surfaces 22c and 25e are provided across the drive shaft 10, and the width d4 of the pair of tilt guide surfaces 22c and 22c of the sleeve 22 is linked. It is wider than the width dO of the one end 45a of the member and the width dO of the other end 45b of the link member (see FIG. 5). Therefore, a larger torsional load can be received by the tilt guide surfaces 22c and 22c of the sleeve 22, and the burden on the link mechanism 40 can be reduced. This further improves the controllability of the compressor.

Landscapes

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

Abstract

La présente invention concerne un compresseur à cylindrée variable qui comprend un élément rotatif (21) qui est fixé à et tourne d’un seul tenant avec un arbre d’entraînement (10), un manchon (22) installé sur l’arbre d’entraînement (10) de façon coulissante dans la direction axiale, un élément d’inclinaison (24) installé de façon rotative sur un manchon (22) par l’intermédiaire d’axes de pivotement (61), un mécanisme de liaison (40) qui relie l’élément rotatif (21) à l’élément d’inclinaison (24) et transmet le couple de rotation de l’élément rotatif (21) à l’élément d’inclinaison (24) tout en permettant l’inclination de l’élément d’inclinaison (24), et des faces de guidage d’inclinaison (22c, 25d) formées sur le manchon (22) et l’élément d’inclinaison (24) en tant que surface perpendiculaire aux axes de pivotement (61) et mises en contact coulissant l’une avec l’autre.
PCT/JP2006/320963 2005-10-27 2006-10-20 Compresseur a cylindree variable WO2007049523A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06812092A EP1942275A4 (fr) 2005-10-27 2006-10-20 Compresseur a cylindree variable
US12/091,662 US20090246050A1 (en) 2005-10-27 2006-10-20 Variable capacity compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005313123A JP4794274B2 (ja) 2005-10-27 2005-10-27 可変容量圧縮機
JP2005-313123 2005-10-27

Publications (1)

Publication Number Publication Date
WO2007049523A1 true WO2007049523A1 (fr) 2007-05-03

Family

ID=37967635

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2006/320963 WO2007049523A1 (fr) 2005-10-27 2006-10-20 Compresseur a cylindree variable

Country Status (6)

Country Link
US (1) US20090246050A1 (fr)
EP (1) EP1942275A4 (fr)
JP (1) JP4794274B2 (fr)
KR (1) KR20080066928A (fr)
CN (1) CN101297115A (fr)
WO (1) WO2007049523A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4974927B2 (ja) * 2008-02-26 2012-07-11 カルソニックカンセイ株式会社 斜板式圧縮機
JP5065120B2 (ja) * 2008-03-28 2012-10-31 サンデン株式会社 往復動圧縮機
JP6063150B2 (ja) * 2012-05-28 2017-01-18 サンデンホールディングス株式会社 可変容量圧縮機
JP6047307B2 (ja) * 2012-05-28 2016-12-21 サンデンホールディングス株式会社 可変容量圧縮機
JP6047306B2 (ja) * 2012-05-28 2016-12-21 サンデンホールディングス株式会社 可変容量圧縮機
JP6171875B2 (ja) * 2013-11-13 2017-08-02 株式会社豊田自動織機 可変容量型斜板式圧縮機
DE112019006499T5 (de) * 2018-12-27 2021-09-23 Hanon Systems Taumelscheibenverdichter

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10176655A (ja) * 1996-12-13 1998-06-30 Zexel Corp 可変容量型斜板式圧縮機
JP2001041153A (ja) * 1999-07-23 2001-02-13 Zexel Valeo Climate Control Corp 可変容量型圧縮機
JP2001304103A (ja) * 2001-03-30 2001-10-31 Zexel Valeo Climate Control Corp 可変容量型圧縮機
JP2001349274A (ja) * 2000-06-07 2001-12-21 Zexel Valeo Climate Control Corp 可変容量型斜板式圧縮機
JP2003172417A (ja) 2001-12-04 2003-06-20 Sanden Corp リンク機構及びそれを用いた可変容量型圧縮機
US20040149058A1 (en) 2003-01-30 2004-08-05 Ebbing David Michael Hinge for a variable displacement compressor
JP2005083325A (ja) * 2003-09-10 2005-03-31 Toyota Industries Corp 回転速度検出機構を備えた容量可変型圧縮機

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4061443A (en) * 1976-12-02 1977-12-06 General Motors Corporation Variable stroke compressor
US4685866A (en) * 1985-03-20 1987-08-11 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement wobble plate type compressor with wobble angle control unit
JPH0329586Y2 (fr) * 1985-11-08 1991-06-24
JPS6365177A (ja) * 1986-09-05 1988-03-23 Hitachi Ltd 可変容量斜板式圧縮機
KR910004933A (ko) * 1989-08-09 1991-03-29 미다 가쓰시게 가변용량사판식 압축기
JP2979687B2 (ja) * 1991-03-26 1999-11-15 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
JPH08326655A (ja) * 1995-06-05 1996-12-10 Calsonic Corp 斜板式コンプレッサ
JPH10176658A (ja) * 1996-12-17 1998-06-30 Zexel Corp 可変揺動板式圧縮機
JPH11125176A (ja) * 1997-10-21 1999-05-11 Calsonic Corp 斜板式可変容量圧縮機
JP2000291541A (ja) * 1999-04-06 2000-10-17 Toyota Autom Loom Works Ltd 可変容量型圧縮機の設計方法及び製造方法
DE10124031B4 (de) * 2001-05-16 2009-08-20 Daimler Ag Hubkolbenmaschine mit einem Mitnehmer

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10176655A (ja) * 1996-12-13 1998-06-30 Zexel Corp 可変容量型斜板式圧縮機
JP2001041153A (ja) * 1999-07-23 2001-02-13 Zexel Valeo Climate Control Corp 可変容量型圧縮機
JP2001349274A (ja) * 2000-06-07 2001-12-21 Zexel Valeo Climate Control Corp 可変容量型斜板式圧縮機
JP2001304103A (ja) * 2001-03-30 2001-10-31 Zexel Valeo Climate Control Corp 可変容量型圧縮機
JP2003172417A (ja) 2001-12-04 2003-06-20 Sanden Corp リンク機構及びそれを用いた可変容量型圧縮機
US20040149058A1 (en) 2003-01-30 2004-08-05 Ebbing David Michael Hinge for a variable displacement compressor
JP2005083325A (ja) * 2003-09-10 2005-03-31 Toyota Industries Corp 回転速度検出機構を備えた容量可変型圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1942275A4

Also Published As

Publication number Publication date
JP2007120394A (ja) 2007-05-17
EP1942275A1 (fr) 2008-07-09
JP4794274B2 (ja) 2011-10-19
KR20080066928A (ko) 2008-07-17
EP1942275A4 (fr) 2010-08-18
CN101297115A (zh) 2008-10-29
US20090246050A1 (en) 2009-10-01

Similar Documents

Publication Publication Date Title
WO2007116936A1 (fr) Compresseur a cylindree variable
WO2007049523A1 (fr) Compresseur a cylindree variable
EP1001169A2 (fr) Compresseur à plateau en biais à capacité variable
US7972118B2 (en) Variable capacity compressor
JP2007239722A (ja) 可変容量型往復動圧縮機
US20070220859A1 (en) Link Mechanism and Variable Displacement Compressor
JPH10266952A (ja) 可変容量型斜板式圧縮機
US20020162720A1 (en) Power transmission mechanism
JP2001304102A (ja) 可変容量圧縮機
JP4451323B2 (ja) リンク機構およびこれを用いた可変容量圧縮機
EP2063121A1 (fr) Compresseur à cylindrée variable
JP4649230B2 (ja) リンク機構および可変容量圧縮機
JP2007278200A (ja) 可変容量圧縮機
US20020182085A1 (en) Power transmitting mechanism
WO2024018829A1 (fr) Compresseur
JP2003049767A (ja) 可変容量型圧縮機
JP2015063892A (ja) 容量可変型斜板式圧縮機
US20020178903A1 (en) Power transmission mechanism
JP6052016B2 (ja) 容量可変型斜板式圧縮機
WO2006095565A1 (fr) Compresseur a cylindree variable
JPH064376U (ja) 可変容量型揺動板式圧縮機のフルストローク位置決め構造
JP2006226192A (ja) 可変容量圧縮機
JP2009257204A (ja) 容量可変型斜板式圧縮機
JP2004044550A (ja) 斜板型圧縮機
JP2006220051A (ja) 可変容量圧縮機

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200680040033.2

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 2006812092

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 1020087009885

Country of ref document: KR

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 12091662

Country of ref document: US