EP1464836A2 - Compresseur à piston axial en particulier CO2-compresseur pour installation de climatisation de véhicule - Google Patents

Compresseur à piston axial en particulier CO2-compresseur pour installation de climatisation de véhicule Download PDF

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Publication number
EP1464836A2
EP1464836A2 EP04006239A EP04006239A EP1464836A2 EP 1464836 A2 EP1464836 A2 EP 1464836A2 EP 04006239 A EP04006239 A EP 04006239A EP 04006239 A EP04006239 A EP 04006239A EP 1464836 A2 EP1464836 A2 EP 1464836A2
Authority
EP
European Patent Office
Prior art keywords
drive shaft
support
swivel plate
support element
compressor according
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.)
Granted
Application number
EP04006239A
Other languages
German (de)
English (en)
Other versions
EP1464836B1 (fr
EP1464836A3 (fr
Inventor
Ottfried Schwarzkopf
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.)
Valeo Compressor Europe GmbH
Original Assignee
Zexel Valeo Compressor Europe GmbH
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=32842263&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1464836(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Zexel Valeo Compressor Europe GmbH filed Critical Zexel Valeo Compressor Europe GmbH
Priority to EP06011772A priority Critical patent/EP1707810A1/fr
Publication of EP1464836A2 publication Critical patent/EP1464836A2/fr
Publication of EP1464836A3 publication Critical patent/EP1464836A3/fr
Application granted granted Critical
Publication of EP1464836B1 publication Critical patent/EP1464836B1/fr
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • F04B27/10—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

Definitions

  • the invention relates to an axial piston compressor, in particular a CO 2 compressor for motor vehicle air conditioning systems, according to the preamble of claim 1.
  • Such an axial piston compressor is for example from DE 197 49 727 A1 known.
  • This comprises a housing in which in a circular arrangement several axial pistons are arranged around a rotating drive shaft.
  • the Driving force is from the drive shaft via a driver to an annular Swivel disc and from this in turn to the parallel to the drive shaft Piston translationally displaceable.
  • the ring-shaped swivel disc is pivotable on an axially displaceably mounted sleeve on the drive shaft stored.
  • An elongated hole is provided in the sleeve through which the driver mentioned round picks.
  • Drive shaft, driver, Sliding sleeve and swivel plate are arranged in a so-called engine room, in the gaseous working medium of the compressor is present at an equipped pressure.
  • the delivery volume and thus the delivery rate of the compressor depend on Pressure ratio between the suction side and pressure side of the pistons or accordingly depending on the pressures in the cylinders on the one hand and in the engine room on the other hand.
  • the driver mentioned serves both for torque transmission between Drive shaft and swivel plate as well as for axial support of the pistons, i.e. for gas power support.
  • the construction according to DE 197 49 727 A1 is based on an older construction, for example according to DE 44 11 926 A1, in which the Driver is formed in two parts, with a first attached to the drive shaft Driver part is arranged at a considerable distance next to the swivel plate and a second driver part engaging in the first in an articulated manner has a lateral part Extension of the swivel plate forms.
  • the disadvantage of this design is that it has axial minimum length of the compressor is significantly determined.
  • An axial piston compressor 1 has, for example, seven pistons 2, which in Arranged circumferentially at the same angular distance from each other and in Cylinder bores 3 of a cylinder block 4 are axially movable back and forth.
  • the stroke movement of the pistons 2 takes place through the engagement of a drive shaft 5 oblique annular swivel plate 6 in engagement chambers 7, the each adjoin closed cavities 8 of the pistons 2.
  • Ball segments or ball segment-like sliding blocks 11 and 12 are provided, so that the swivel plate 6 slides between them as it rotates.
  • the drive transmission from the drive shaft 5 to the annular swivel plate 6 takes place through a driver bolt 13 fastened in the drive shaft 5, the latter, for example spherical head in a radial bore 16 of the annular swivel disk 6 intervenes.
  • the position of the driver head 15 is curled so that its Center point 17 with that of the spherical shape of the spherical segments 11, 12 matches. In addition, this center lies on a circular line, the geometric axes of the seven pistons. In this way the dead center position of the pistons 2 is precisely determined and a minimal harmful one Space guaranteed.
  • the head shape of the free driver end enables the inclination of the to be changed annular swivel plate 6 by the driving head 15 a bearing body for the swiveling movement of the swash plate 6 changing the stroke width of the pistons 2 forms.
  • Another prerequisite for pivoting the disc 6 is Slidability of its bearing axis 20 in the direction of the drive shaft 5. This is 11, the bearing axis 20 by two coaxially on both sides one Sliding sleeve 21 bearing bolts 22, 23 formed, which also in radial Bores 24, 25 of the annular swivel plate 6 are mounted.
  • the sliding sleeve 21 preferably has bearing sleeves 26, 27 on both sides which define the annular space 28 bridge between the sliding sleeve 21 and the annular swivel disk 6.
  • the limitation of the displaceability of the bearing axis 20 and the maximum Inclination of the swivel plate 6 results from the driving pin 13, by penetrating an elongated hole 30 provided in the sliding sleeve 21, so that the sliding sleeve 21 finds 30 stops at the ends of the elongated hole.
  • the power for the angular adjustment of the swivel plate 6 and thus for a regulation of the Compressor results from the sum of the pistons 2 on both sides opposing pressures so that this force from the pressure in the engine room 33 is dependent.
  • a flow connection can be used to regulate this pressure be provided with an external source of pressurized gas.
  • the setting of the position of the Sliding sleeve 21 and thus the stroke of the piston 2 or the delivery rate of the Compressor is carried out by at least one interacting with the sliding sleeve 21 Spring 34, 35.
  • the sliding sleeve 21 is between two Helical compression springs 34, 35 included, which are arranged on the drive sleeve 5 are.
  • a disadvantage of the known construction is that the contact principle described non-uniform deformation behavior between the driver and the swashplate of the swashplate running sides, which subsequently results in one leads to unfavorable running behavior of the sliding blocks on the swivel plate.
  • the cylindrical bore of the swash plate in which the spherical end of the Carrier supports, it comes due to the very small residual wall thickness to a strong deformation in this area. This will change the running properties the sliding blocks on the swivel plate are impaired accordingly.
  • This problem has already been recognized. To avoid this, for example, in the WO 02/38959 A1 different geometrical shapes between drivers and associated mounting hole have been proposed.
  • swash plate engine is known from FR 2 782 126 A1 which a driver protrudes into a swivel plate.
  • the swivel plate is also radial Articulated direction and therefore has no displacement in the radial direction.
  • the advantage of this design is that the associated joint has the forces can be transferred across the surface, with the result that a relatively small construction is possible.
  • the well-known driver / torque arm is both by the torque acted upon as well as by the support force of the swash plate in response to resulting gas forces. Both force and bending moment curves show their maximum in the area of the mount on the drive shaft. Accordingly, the Drive shaft must be dimensioned. The same naturally also applies to the dimensioning both the driver and the swivel plate, especially in the area of Location hole for the driver. The stronger dimensioning naturally leads inevitably to correspondingly higher masses and thus moments of inertia. This can adversely affect the control behavior and must be compensated. The stronger dimensioning also means that the pistons are assigned Joint arrangements are dimensioned larger or are dimensioned larger have to. This applies to both the sliding blocks and the pistons themselves.
  • the present invention is based on the object To create compressors of the type mentioned, which without restriction Functional reliability can be built more easily.
  • the compressor 100 shown in FIG. 1 in a schematic longitudinal section comprises one Cylinder block 101, a housing 102 delimiting an engine room 103 and a drive shaft 104, which via a swivel plate mechanism 105 inside of the engine room 103 several, in particular seven evenly over the circumference drives axial pistons 106 arranged around the drive shaft 104, which inside of the cylinder block 101 are axially displaceably mounted.
  • the swivel plate mechanism 105 comprises an annular swivel plate 107, both with an axially displaceably mounted on the drive shaft 104 Sliding sleeve 108 and with a distance from the drive shaft 104 with this pivoting support element 109 is pivotally connected, the piston 106 each have a joint arrangement 110 on which the annular swivel disk 107 is in sliding engagement.
  • the hinge arrangement 110 is corresponding to FIG trained according to the prior art and also comprises two semi-spherical Sliding blocks 111, 112.
  • the sliding sleeve 108 is also formed as in the prior art and through Helical compression springs 113 axially preloaded.
  • the support element 109 is in the embodiment shown as a spherical head educated. This is located at the free end of a pin-like power transmission element 114.
  • the support member 109 engages in an annular swivel plate 107, namely an elongated hole 115 formed on the ring element thereof a whose bore axis is radial and whose longer cross-sectional axis is in Extends circumferential direction. This ensures that the support element 109 in the essential only for the axial support of the pistons 106 or for gas force support serves.
  • the corresponding forces are assigned via the support element and the Transfer power transmission pin 114 to the drive shaft 104.
  • the Torque transmission between drive shaft 104 and swash plate 107 takes place exclusively via an articulated connection 116 arranged between them (see figures 2 to 5).
  • the support element 109 can also be cylindrical or barrel-shaped instead of spherical be trained. In the latter two cases, the longitudinal axis extends of the support element perpendicular to the pin-like force transmission element 114.
  • This Embodiment has the advantage that the axial support via a line contact between the support element and the corresponding radial bore in the swivel plate 107 takes place.
  • the swivel joint 116 between the drive shaft 104 and swivel plate 107 can have different designs, as can be seen in FIGS. 2 to 5. These figures also show that the support element 109 is inside the elongated hole 115 has sufficient play in the circumferential or rotational direction, so that forces due to the drive torque are never effective. By the support element is only absorbed and transmitted axial gas forces.
  • the torque transmission takes place between Drive shaft 104 and annular swivel plate 107 over two relative to Drive shaft 104 diametrically extending bolts between sliding sleeve 108th and swivel plate 107 are effective.
  • the sliding sleeve itself is over one Key arrangement 117 is connected in a rotationally fixed manner to the drive shaft 104.
  • the annular swivel plate 107 is around by the bearing bolts 118th defined axis pivotable.
  • the pin-like power transmission element 114 extends through the sliding sleeve 108 with play.
  • the anti-rotation lock takes place between Sliding sleeve 108 and drive shaft 104 through the pin-like power transmission element 114. Otherwise, the construction according to FIG. 3 coincides with that 2.
  • the embodiment according to FIG. 4 essentially corresponds to that according to FIG. 3; because also in the embodiment according to FIG. 4, the anti-rotation lock takes place between Drive shaft 104 and sliding sleeve 108 through the power transmission pin 114. Die Coupling takes place in the embodiment of FIG. 4 only on the spherical support member 109 opposite end of the power transmission pin 114th
  • FIG. 5 shows a further solution for the connection between drive shaft 104 and annular swivel plate 107, without the interposition of hinge pins 118.
  • These are in the embodiment according to FIG. 5 by corresponding Radial journal 119 of the sliding sleeve 108 replaced.
  • These radial pins 119 define one Swivel bearing for the annular swivel plate 107 around by the radial pin 119 defined transverse axis 120. Otherwise, the construction according to FIG. 5 corresponds that of FIG. 2.
  • Figures 6 and 7 show two different embodiments for the Connection between a spherical support element 109 and a pin-like Power transmission element 114.
  • this is spherical Support member 109 at one end of a sleeve-like power transmission element 114 arranged, in particular welded (preferably friction welding connection).
  • the pin-like force transmission element 114 still a ring heel 121, which acts as a stop for the introduction in a receiving bore formed in the drive shaft 104 is used.
  • the pen-like Power transmission element 114 is arranged in the embodiment according to FIG. 1, that it protrudes obliquely from the drive shaft 104, in such a way that at a middle inclination position of the annular swivel plate 107 the longitudinal axis of the pin-like power transmission element 114 radially to the annular swivel plate 107 is directed.
  • the abovementioned stop 121 also ensures, moreover, that the center 122 of the spherical support element 109 coincides with the center of the joint arrangement 110 assigned to each piston without additional adjustment measures during the assembly of the compressor.
  • This installation position is preferred; however, it can also be advantageous to provide a slight “off” of up to approximately 1/10 mm between the circular line on which the center point of the support element 109 on the one hand and the circular line on which the center points of the piston joint arrangements 110 lie on the other hand to vary the clearance slightly depending on the swivel angle.
  • the center point 122 of the support element 109 preferably lies on a circular line that extends radially slightly outside the circular line on which the center points of the piston-joint arrangement 110 lie. This embodiment has the advantage that at no time do tilt moments act on the swivel plate, which tilt the swivel plate in a different, unintended direction.
  • FIG. 8 shows a further exemplary embodiment of a compressor according to the invention, at the parts that have already been described with reference to FIG. 1 with the same reference numbers as marked in Fig. 1.
  • the swivel plate mechanism 105 is in the exemplary embodiment according to FIG. 8 identical. 8 differs from that 1 essentially only in that the cylinder block 101 is in the Engine room 103 extends conically into it, thereby extending the guidance of the Piston 106 is reached.
  • the cone 123 is designed so that it fits into the Annulus 124 between sliding sleeve 108 and annular swivel disk 107 hineinerstreckt. This allows the compressor to be built with regard to its overall length reduce additionally.
  • the support element 109 is a at the free end L-shaped power transmission element 114 arranged at the free end of the shorter leg 125, which extends obliquely radially outwards.
  • the longer one Leg 126 extends approximately parallel to the drive shaft 104 and is axially on one supported with the drive shaft 104 rotatably connected support plate 127.
  • the Support disk 127 is in turn around the drive shaft 104 extending needle bearing 128 supported on the housing 102.
  • This construction has the advantage that there is a reveal in the drive shaft 104 can be avoided for the pin-like power transmission element 114. Accordingly, the diameter of the drive shaft 104 can be greatly reduced become.
  • Fig. 9 also makes it clear that the so-called gas force support can alternatively also from the outside instead of engaging inside the swashplate, in which case the Piston rotation lock not on the inside of the engine housing 102, but instead would be shifted inwards to the drive shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP04006239A 2003-04-04 2004-03-16 Compresseur à piston axial en particulier CO2-compresseur pour installation de climatisation de véhicule Revoked EP1464836B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06011772A EP1707810A1 (fr) 2003-04-04 2004-03-16 Compresseur à piston axial en particulier CO2-compresseur pour installation de climatisation de véhicule

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10315477 2003-04-04
DE10315477A DE10315477B4 (de) 2003-04-04 2003-04-04 Axialkolbenverdichter, insbesondere CO2-Verdichter für Kraftfahrzeug-Klimaanlagen

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP06011772A Division EP1707810A1 (fr) 2003-04-04 2004-03-16 Compresseur à piston axial en particulier CO2-compresseur pour installation de climatisation de véhicule

Publications (3)

Publication Number Publication Date
EP1464836A2 true EP1464836A2 (fr) 2004-10-06
EP1464836A3 EP1464836A3 (fr) 2005-02-09
EP1464836B1 EP1464836B1 (fr) 2006-12-20

Family

ID=32842263

Family Applications (2)

Application Number Title Priority Date Filing Date
EP06011772A Ceased EP1707810A1 (fr) 2003-04-04 2004-03-16 Compresseur à piston axial en particulier CO2-compresseur pour installation de climatisation de véhicule
EP04006239A Revoked EP1464836B1 (fr) 2003-04-04 2004-03-16 Compresseur à piston axial en particulier CO2-compresseur pour installation de climatisation de véhicule

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP06011772A Ceased EP1707810A1 (fr) 2003-04-04 2004-03-16 Compresseur à piston axial en particulier CO2-compresseur pour installation de climatisation de véhicule

Country Status (3)

Country Link
US (1) US7490540B2 (fr)
EP (2) EP1707810A1 (fr)
DE (2) DE10315477B4 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006037356A1 (fr) * 2004-10-01 2006-04-13 Zexel Valeo Compressor Europe Gmbh Machine presentant des pistons a mouvement de va-et-vient, en particulier compresseur destine a une unite de conditionnement d'air de vehicule
EP1693567A1 (fr) * 2003-11-14 2006-08-23 Valeo Thermal Systems Japan Corporation Compresseur de type plateau oscillant
WO2009121553A1 (fr) * 2008-04-04 2009-10-08 Schaeffler Kg Compresseur, en particulier pour des installations de climatisation pour véhicule automobile

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112005002570A5 (de) * 2004-11-05 2007-07-12 Ixetic Mac Gmbh Hubkolbenmaschine
DE102005004840A1 (de) * 2005-02-02 2006-08-10 Valeo Compressor Europe Gmbh Axialkolbenverdichter
DE102005018102A1 (de) 2005-04-19 2005-11-03 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter
US20060285981A1 (en) * 2005-06-21 2006-12-21 Visteon Global Technologies, Inc. Swash ring compressor with spherical bearing
US7444921B2 (en) * 2006-08-01 2008-11-04 Visteon Global Technologies, Inc. Swash ring compressor
US7802512B2 (en) * 2007-02-07 2010-09-28 Doowon Technical College Assembly structure of drive shaft and swash plate in swash plate type compressor
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

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US2809868A (en) * 1953-10-01 1957-10-15 Sabre Res Corp Fuel pump and fuel injector combination
US2955475A (en) * 1957-01-10 1960-10-11 Gen Motors Corp Variable pressure fluid pump
US3861829A (en) * 1973-04-04 1975-01-21 Borg Warner Variable capacity wobble plate compressor
US4886423A (en) * 1986-09-02 1989-12-12 Nippon Soken, Inc. Variable displacement swash-plate type compressor
JPH05172046A (ja) * 1991-12-19 1993-07-09 Toyota Autom Loom Works Ltd 揺動斜板式可変容量圧縮機
DE10010132A1 (de) * 2000-03-03 2001-10-04 Luk Fahrzeug Hydraulik Hubkolbenmaschine

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US2964234A (en) * 1954-05-13 1960-12-13 Houdaille Industries Inc Constant clearance volume compressor
US4815943A (en) * 1986-10-01 1989-03-28 Hitachi, Ltd. Variable displacement wobble plate compressor with capacity control valve
JPS63186973A (ja) * 1987-01-30 1988-08-02 Hitachi Ltd 可変ストロ−ク斜板式圧縮機
KR910004933A (ko) * 1989-08-09 1991-03-29 미다 가쓰시게 가변용량사판식 압축기
JPH0552183A (ja) * 1991-08-21 1993-03-02 Hitachi Ltd 可変容量形圧縮機
US5417552A (en) * 1992-10-20 1995-05-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
JP3125952B2 (ja) * 1993-04-08 2001-01-22 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
JPH09112420A (ja) * 1995-10-19 1997-05-02 Toyota Autom Loom Works Ltd 可変容量圧縮機
JP3422186B2 (ja) * 1995-11-24 2003-06-30 株式会社豊田自動織機 可変容量圧縮機
JP3826473B2 (ja) * 1997-02-28 2006-09-27 株式会社豊田自動織機 可変容量型圧縮機
JPH10266952A (ja) * 1997-03-25 1998-10-06 Zexel Corp 可変容量型斜板式圧縮機
DE19749727C2 (de) * 1997-11-11 2001-03-08 Obrist Engineering Gmbh Lusten Hubkolbenmaschine mit Schwenkscheibengetriebe
FR2782126B1 (fr) * 1998-08-10 2000-10-13 Valeo Climatisation Compresseur a cylindree variable
JP3479233B2 (ja) * 1999-03-11 2003-12-15 サンデン株式会社 可変容量斜板式圧縮機のカム機構
JP2002031043A (ja) * 2000-07-14 2002-01-31 Toyota Industries Corp 圧縮機
WO2002038959A1 (fr) * 2000-11-10 2002-05-16 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Machine a piston alternatif

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2809868A (en) * 1953-10-01 1957-10-15 Sabre Res Corp Fuel pump and fuel injector combination
US2955475A (en) * 1957-01-10 1960-10-11 Gen Motors Corp Variable pressure fluid pump
US3861829A (en) * 1973-04-04 1975-01-21 Borg Warner Variable capacity wobble plate compressor
US4886423A (en) * 1986-09-02 1989-12-12 Nippon Soken, Inc. Variable displacement swash-plate type compressor
JPH05172046A (ja) * 1991-12-19 1993-07-09 Toyota Autom Loom Works Ltd 揺動斜板式可変容量圧縮機
DE10010132A1 (de) * 2000-03-03 2001-10-04 Luk Fahrzeug Hydraulik Hubkolbenmaschine

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Title
PATENT ABSTRACTS OF JAPAN Bd. 0175, Nr. 84 (M-1501), 25. Oktober 1993 (1993-10-25) & JP 5 172046 A (TOYOTA AUTOM LOOM WORKS LTD), 9. Juli 1993 (1993-07-09) *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1693567A1 (fr) * 2003-11-14 2006-08-23 Valeo Thermal Systems Japan Corporation Compresseur de type plateau oscillant
EP1693567A4 (fr) * 2003-11-14 2007-10-24 Valeo Thermal Sys Japan Co Compresseur de type plateau oscillant
WO2006037356A1 (fr) * 2004-10-01 2006-04-13 Zexel Valeo Compressor Europe Gmbh Machine presentant des pistons a mouvement de va-et-vient, en particulier compresseur destine a une unite de conditionnement d'air de vehicule
WO2009121553A1 (fr) * 2008-04-04 2009-10-08 Schaeffler Kg Compresseur, en particulier pour des installations de climatisation pour véhicule automobile

Also Published As

Publication number Publication date
US20040216603A1 (en) 2004-11-04
EP1464836B1 (fr) 2006-12-20
DE502004002343D1 (de) 2007-02-01
DE10315477B4 (de) 2005-08-11
DE10315477A1 (de) 2004-10-21
EP1464836A3 (fr) 2005-02-09
US7490540B2 (en) 2009-02-17
EP1707810A1 (fr) 2006-10-04

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