EP1693567A1 - Taumelscheiben-verdichter - Google Patents

Taumelscheiben-verdichter Download PDF

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Publication number
EP1693567A1
EP1693567A1 EP04792257A EP04792257A EP1693567A1 EP 1693567 A1 EP1693567 A1 EP 1693567A1 EP 04792257 A EP04792257 A EP 04792257A EP 04792257 A EP04792257 A EP 04792257A EP 1693567 A1 EP1693567 A1 EP 1693567A1
Authority
EP
European Patent Office
Prior art keywords
drive member
shaft
rotational drive
link pin
sleeve
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Withdrawn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
EP04792257A
Other languages
English (en)
French (fr)
Other versions
EP1693567A4 (de
Inventor
Hiroshi VALEO THERMAL SYSTEMS JAPAN CORP. KANAI
Hironobu VALEO THERMAL SYSTEMS JAPAN CORP DEGUCHI
Shunichi VALEO THERMAL SYSTEMS JAPAN CORP. FURUYA
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 Thermal Systems Japan Corp
Original Assignee
Valeo Thermal Systems Japan 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 Valeo Thermal Systems Japan Corp filed Critical Valeo Thermal Systems Japan Corp
Publication of EP1693567A1 publication Critical patent/EP1693567A1/de
Publication of EP1693567A4 publication Critical patent/EP1693567A4/de
Withdrawn legal-status Critical Current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
    • 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

Definitions

  • the present invention relates to a swash plate compressor comprising a rotational drive member that is housed inside a crankcase and is caused to rotate as a shaft rotates and a piston that is held at the peripheral edge of the rotational drive member and is caused to reciprocally slide inside a cylinder as the rotational drive member rotates, which controls the delivery displacement by adjusting the angle of inclination of the rotational drive member. More specifically, it relates to a compressor with its shaft and rotational drive member linked via a link mechanism.
  • Compressors of similar types known in the related art include the swash plate compressor adopting the structure described in patent reference literature 1.
  • the compressor comprises a cylinder block 1, a rear head 3 mounted on the rear side (the left side in FIG. 5) of the cylinder block 1 via a valve plate 2 and a front head 5 mounted so as to close off the front side (the left side in FIG. 5) of the cylinder block 1, thereby defining a crankcase 4, as shown in FIG. 5.
  • the front head 5, the cylinder block 1, the valve plate 2 and the rear head 3 constitute a housing.
  • a shaft 6 with one end thereof projecting out of the front head 5 and locked with a motive power communicating member such as a pulley (not shown) is housed.
  • the one end of the shaft 6 extends so as to pass through a boss portion 5a of the front head 5 projecting outward at the center thereof.
  • the one end of the shaft 6 is rotatably supported via a radial bearing 7 and a shaft seal 8 disposed over the inner surface of the boss portion 5a and also via a thrust bearing 9 disposed over the inner surface of the front head 5.
  • the other end of the shaft 6 is rotatably supported at an indented portion 10 formed at the center of the cylinder block 1 via a radial bearing 11 and a thrust bearing 12.
  • the indented portion 10 at which the shaft 6 is inserted and a plurality of cylinders 13 disposed over equal intervals on the circumference of a circle centering around the indented portion 10 are formed.
  • a single-ended piston 14 is inserted at each cylinder 13 so as to reciprocally slide therein.
  • a rotational drive member (annular disk) 16 is tiltably connected to the shaft 6 via a link pin (driver) 15, and the tail end 14a of the piston 14 projecting out into the crankcase 4 is held at the peripheral edge of the rotational drive member 16 via a pair of shoes 17.
  • the rotational drive member 16 also rotates in synchronization, the rotational motion of the rotational drive member is then converted to a reciprocal linear motion of the piston 14 via the shoes 17, and as the piston 14 moves reciprocally, the volumetric capacity of a compression space formed inside the cylinder 13 between the piston 14 and the valve plate 2 is altered.
  • the link pin 15 is disposed at a middle portion 6a of the shaft 6 facing the crankcase 4.
  • a flange portion 6b formed at the end thereof on the front side is rotatably supported at the inner surface of the front head 5 via the thrust bearing 9.
  • the end of the middle portion 6a on the rear side is rotatably supported at the opposite surface at the cylinder block 1 via the thrust bearing 12.
  • the link pin 15, which is fixed onto the flat surface containing the axial center of the shaft 6, includes a base portion 15a fixed in an insertion hole 6c formed at the middle portion 6a through press-fitting or the like, a small diameter portion 15b continuous from the base portion 15a and a head 15c assuming a spherical shape at a free end continuous from the small diameter portion 15b.
  • the annular disk 16 includes an engaging hole 16a opening inward along the radial direction, and with the head 15c of the link pin 15 engaged at the engaging hole 16a the drive force from the shaft 6 is communicated via the link pin 15.
  • a sliding sleeve 20 is externally fitted on the shaft so as to slide freely along the axial direction.
  • the sliding sleeve 20 includes arms 20a extending in the radial direction, which bridge across the annular disk 16 like spokes via supporting pins 21.
  • a longitudinal hole 20b, at which the link pin 15 is inserted without inhibiting the sliding motion of the shaft 6 along the axial direction is formed at the sliding sleeve 20.
  • the head 15c of the link pin 15 rotating together with the shaft 6 presses against the inner surface of the engaging hole 16a at the annular disk 16, and the rotational motive power from the shaft 6 is communicated to the annular disk 16 via the link pin 15. Then, as the annular disk 16 rotates around the supporting pins 21, the sleeve 20 moves along the axis of the shaft 6 and the contact position at which the head 15c of the link pin 15 contacts moves along the axis of the engaging hole 16a.
  • Patent reference literature 1 Patent Publication No. 3188716
  • the supporting pins 21 each bridging between a supporting hole 16c at the annular disk 16 and a supporting hole 20c at the sliding sleeve 20 are press-fitted inside the supporting holes on both sides, the tilting motion of the annular disk 16 is inhibited, whereas if the supporting pins are loosely inserted at the supporting holes on both sides, the supporting pins 21 may become misaligned or fall out.
  • a main object of the present invention which has been completed by addressing the problems discussed above, is to improve the durability over an area where a link pin is engaged in a swash plate compressor having a shaft and a rotational drive member linked via the link pin.
  • Another object of the present invention is to achieve a smooth tilting motion of the rotational drive member.
  • the swash plate compressor comprising a shaft passing through a crankcase and rotatably supported at a housing, a rotational drive member having an opening through which the shaft is inserted and disposed in the crankcase to rotate synchronously as the shaft rotates and a piston held at the peripheral edge of the rotational drive member, which reciprocally slides inside a cylinder formed at the housing as the rotational drive member rotates, with the piston stroke varied by adjusting the angle of inclination of the rotational drive member, and characterized in that the rotational drive member is tiltably linked to the shaft via a link pin and that the rotational motive power of the shaft is communicated via a portion other than the head of the link pin.
  • the rotational motive power is communicated to the rotational drive member via a portion other than the head of the link pin.
  • the rotational drive member is allowed to rotate without having to press the head of the link pin against the rotational drive member, lowering the extent of wear over the engaging area facing the head.
  • the swash plate compressor may adopt a structure in which an engaging hole with one end thereof opening at the opening and the other end thereof opening toward the outer circumference is formed at the rotational drive member, the head of the link pin is slidably inserted at the engaging hole so as to allow a tilting motion of the rotational drive member, a sleeve is externally fitted at the shaft so as to allow the sleeve to slide freely, a pass hole through which the link pin is inserted is formed at the sleeve, the rotational drive member is tiltably supported at the sleeve via a supporting pin and the clearance formed between the inner surface of the pass hole at the sleeve and a base of the link pin is set smaller than the clearance formed along the shaft rotating direction between the inner surface of the engaging hole and the head of the link pin.
  • the base of the link pin comes into contact with the sleeve as the shaft rotates, allowing the rotational motive power to be communicated from the sleeve to the rotational drive member via the supporting pin.
  • the rotational drive member can rotate without the head of the link pin pressed against the rotational drive member along the shaft rotating direction.
  • the swash plate compressor may adopt a structure in which an engaging hole with one end thereof opening at the opening and the other end thereof opening toward the outer circumference is formed at the rotational drive member, the head of the link pin is slidably inserted at the engaging hole so as to allow a tilting motion of the rotational drive member, a sleeve is externally fitted at the shaft so as to allow the sleeve to slide freely, a pass hole through which the link pin is inserted is formed at the sleeve, the rotational drive member is tiltably supported at the sleeve via a supporting pin passing through a pass hole formed at the shaft and the clearance formed between the inner surface of the pass hole at the shaft and the supporting pin is set smaller than the clearance formed along the shaft rotating direction between the inner surface of the engaging hole and the head of the link pin.
  • the rotational motive power is directly communicated from the shaft to the rotational drive member via the supporting pin.
  • the rotational drive member can rotate without the head or the base of the link pin pressed against the rotational drive member or the sleeve along the shaft rotating direction.
  • the engaging hole in the structure described above may have a circular section or an elliptical section and that the rotational drive member and the sleeve may be simply linked via the supporting pin without actually contacting each other.
  • the supporting pin may be press-fitted and fixed at either the rotational drive member or the sleeve in order to assure a smooth tilting motion of the rotational drive member. It is desirable that the clearance between the side of the supporting pin where it is press-fitted and the insertion area on the opposite side be set smaller than the clearance formed along the rotating direction between the inner surface of the engaging hole and the head of the link pin.
  • the shaft is linked to the rotational drive member via a link pin so as to allow the rotational drive member to engage in a tilting motion and the rotational motive power of the shaft is communicated to the rotational drive member via a portion other than the head of the link pin.
  • the head of the link pin is not pressed against the inner surface of the engaging hole, thereby preventing the link pin head from wearing the inner surface of the engaging hole.
  • the head of the link pin is slidably inserted at the engaging hole so as to allow a tilting motion of the rotational drive member, a sleeve is externally fitted at the shaft so as to allow the sleeve to slide freely, a pass hole through which the link pin is inserted is formed at the sleeve, the rotational drive member is tiltably supported at the sleeve via a supporting pin and the clearance formed between the inner surface of the pass hole at the sleeve and the base of the link pin is set smaller than the clearance formed along the shaft rotating direction between the inner surface of the engaging hole and the head of the link pin, the rotational motive power of the shaft can be communicated to the rotational drive member via the link pin base and the supporting pin, while avoiding contact between the link pin head and the inner surface of the engaging portion along the shaft rotating direction, which, in turn,
  • the head of the link pin is slidably inserted at the engaging hole so as to allow a tilting motion of the rotational drive member, a sleeve is externally fitted at the shaft so as to allow the sleeve to slide freely, a pass hole through which the link pin is inserted is formed at the sleeve, the rotational drive member is tiltably supported at the sleeve via a supporting pin passing through a pass hole formed at the shaft and the clearance formed between the inner surface of the pass hole at the shaft and a base of the supporting pin is set smaller than the clearance formed along the shaft rotating direction between the inner surface of the engaging hole and the head of the link pin, the rotational motive power of the shaft can be communicated to the rotational drive member via the supporting pin alone, thereby avoiding contact between the link pin head and the inner surface of the engaging portion and contact between the link pin
  • the clearance between the side where the supporting pin is press-fitted and the insertion area on the opposite side may be set smaller than the clearance formed along the rotating direction between the inner surface of the engaging hole and the link pin head so as to communicate the rotational motive power reliably via the supporting pin while preventing contact between the link pin hand and the inner surface of the engaging hole with a higher level of reliability.
  • FIG. 1 shows the structure adopted in a motive power communicating mechanism for a rotational drive member 16 used in the swash plate compressor described earlier.
  • the rotational drive member 16 in the figure is tiltably linked to a shaft 6 via a link pin 15 locked onto the shaft 6 and assumes a ring-shape with an opening 22 through which the shaft 6 is inserted formed at the center thereof.
  • an engaging hole 16a with one end thereof opening at the opening 22 and the other end thereof opening toward the outer circumference is formed.
  • the link pin 15 is slidably inserted at the engaging hole 16a so as to allow the rotational drive member 16 to tilt.
  • the link pin 15 which includes a base 15a fixed at an insertion hole 6c formed at the shaft 6 through press-fitting or screwing, a small-diameter portion 15b formed continuous to the base 15a and a head 15c assuming a spherical shape at a free end continuous to the small diameter portion 15b tolerates the tilting motion of the rotational drive member 16 with the head 15c engaged at the engaging hole 16a formed at the rotational drive member 16.
  • Arms 20a projecting along the radial direction on the two sides of the shaft 6, are formed as integrated parts of a sleeve 20, which is slidably fitted over the exterior of the shaft 6.
  • the arms 20a do not extend far enough to come into contact with the inner surface of the rotational drive member 16 and are linked with the rotational drive member 16 via supporting pins 21 each bridging between a supporting hole 20c formed at an arm 20a and a supporting hole 16c formed at the rotational drive member 16 at a position facing opposite the arm 20a so as to be allowed to rotate relative to the rotational drive member 16.
  • the rotational drive member 16 is linked to the sleeve so that it is allowed to tilt around the supporting pins.
  • the supporting pins 21 are each press-fitted either in the supporting hole 20c at the arm 20a or in the supporting hole 16c at the rotational drive member 16 and are each loosely inserted at the other supporting hole. Thus, the supporting pins 21 do not fall out or become misaligned, while assuring a smooth tilting motion of the rotational drive member 16.
  • the clearance L1 between a longitudinal hole 20b at the sleeve 20 and the base of the link pin 15 ranging along the direction in which the shaft 6 rotates is set smaller than the clearance L2 between the head 15c of the link pin 15 and the inner surface of the engaging hole facing the head 15c along the rotating direction, and thus, the base of the link pin 15 is allowed to come into contact with the sleeve 20 readily as the shaft 6 rotates.
  • a sliding layer constituted with a solid lubricating agent such as PTFE may be formed at least either of the contact surfaces, i.e., either the inner surface of the longitudinal hole 20b or the surface at the base of the link pin 15.
  • the clearance between the sliding layer and the portion facing the sliding layer is equivalent to the clearance L1 described earlier.
  • Such a structure may be achieved by forming the engaging hole 16a so as to achieve a circular section with a greater diameter than the diameter of the head, as in this example.
  • the engaging hole 16a may be formed so as to have an elliptical section elongated along the rotating direction, thereby forming a non-contact area along the rotating direction as illustrated in the upper right insert in FIG. 1.
  • the clearance L3, formed along the rotating direction on the side (the side toward the rotational drive member in this example) opposite from the side where the supporting pins 21 are press-fitted is set smaller than the clearance L2 formed between the head of the link pin and the inner surface of the engaging hole 16a facing the head along the direction in which the shaft 6 rotates and also, the sum L1 + L3 is smaller than L2 in the structure described above.
  • the base 15a of the link pin 15 comes into contact with the inner surface of the longitudinal hole 20b at the sleeve 20, the supporting pins 21 come into contact with the inner surfaces along the rotating direction of either the supporting holes 16c at the rotational drive member 16 or the supporting holes 20c at the sleeve 20 where the supporting pins 21 are loosely held, and the rotational motive power is communicated to the rotational drive member 16 via the link pin 15 and the supporting pins 21.
  • the head 15c of the link pin 15 is not pressed against the inner surface of the engaging hole 16a at the rotational drive member 16 even when the shaft 6 rotates, thereby eliminating the problem of significant wear at the inner surface of the engaging hole 16a caused by the head 15c of the link pin 15 and improving the durability of the rotational drive member 16.
  • the link pin 15 described above may be mounted by embedding the tip of the base 15a in the shaft 6 as shown in FIG. 5, or it may be mounted as shown in FIG. 2 by inserting the end of the link pin passing through the shaft 6 and projecting beyond the shaft 6 at a longitudinal hole 20d formed on the side opposite from the longitudinal hole 20b at the sleeve 20, setting the clearance L1 formed along the rotational direction between the inner surfaces of the longitudinal holes 20b and 20d and the base 15a of the link pin 15 smaller than the clearance L2 between the head 15c of the link pin 15 and the inner surface of the engaging hole 16a facing the head 15c along the rotational direction and allowing the base 15a of the link pin 15 to come into contact with the sleeve 20 at the two positions as the shaft rotates.
  • the rotational load of the link pin 15 is bourn at the two positions of the sleeve 20, and thus, an improvement in the durability at the contact areas is achieved by reducing the extent of wear.
  • FIGS. 3 and 4 present another structural example that may be adopted when linking the rotational drive member 16 to the sleeve 20.
  • a pass hole 30 with an elliptical section which extends along a direction running perpendicular to the axial center of the shaft 6 and ranges over a predetermined length along the axial direction is formed at the shaft 6, an engaging hole 20c with a circular section is formed at the arms 20a of the sleeve 20 so as to align with the pass hole 30 and a supporting pin 21 longer than the diameter of the opening 22 is inserted so as to pass through the pass hole 30 at the shaft 6 and the engaging hole 20c at the sleeve 20. Then, the supporting pin 21 is inserted at the supporting holes 16c at the rotational drive member 16 so as to tiltably hold the rotational drive member at the sleeve.
  • the supporting pin 21 in the structure is press-fitted either at the sleeve 20 or at the rotational drive member 16 and is loosely held at the other member.
  • the clearance (the clearance over the area enclosed with the dotted line in FIG. 3) L4 formed along the rotating direction over the area where the supporting pin 21 passes through the pass hole 30 at the shaft 6 is set smaller than the clearance L2 formed between the head 15a of the link pin 15 and the inner surface of the engaging hole 16a facing the head along the rotating direction or the clearance L1 formed along the rotating direction between the longitudinal hole 20b at the sleeve 20 and the base 15a of the link pin 15.
  • the clearance (the clearance formed on the side toward the rotational drive member in this example) L3 over the area on the side where the supporting pin 21 is not pressed-fitted is set smaller than the clearance L2 between the head 15c of the link pin 15 and the inner surface of the engaging hole 16a facing the head along the direction in which the shaft 6 rotates, and the sum L1+ L3 is smaller than L2.
  • the overall structure ensures that as the shaft 6 rotates, the head 15c of the link pin 15 does not come into contact with the inner surface of the engaging hole 16a along the rotating direction.
  • the rotational motive power of the shaft 6 is communicated to the rotational drive member 16 via the supporting pin 21 alone without the link pin 15 ever coming into contact with the rotational drive member 16 or the sleeve 20 along the rotating direction.
  • the inner surface of the engaging hole 16a or the sleeve 20 over the longitudinal hole does not become worn, which assures an improvement in the durability of the sleeve 20 as well as the durability of the rotational drive member 16.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP04792257A 2003-11-14 2004-10-12 Taumelscheiben-verdichter Withdrawn EP1693567A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003384797A JP2005146968A (ja) 2003-11-14 2003-11-14 斜板式圧縮機
PCT/JP2004/015012 WO2005047697A1 (ja) 2003-11-14 2004-10-12 斜板式圧縮機

Publications (2)

Publication Number Publication Date
EP1693567A1 true EP1693567A1 (de) 2006-08-23
EP1693567A4 EP1693567A4 (de) 2007-10-24

Family

ID=34587336

Family Applications (1)

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EP04792257A Withdrawn EP1693567A4 (de) 2003-11-14 2004-10-12 Taumelscheiben-verdichter

Country Status (3)

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EP (1) EP1693567A4 (de)
JP (1) JP2005146968A (de)
WO (1) WO2005047697A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105114278A (zh) * 2015-07-24 2015-12-02 杭州绿聚科技有限公司 一种新型轴向柱塞泵

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
KR100922123B1 (ko) 2007-03-06 2009-10-16 학교법인 두원학원 사판식 압축기에서의 구동축과 사판의 연결구조
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

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1464836A2 (de) * 2003-04-04 2004-10-06 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter, insbesondere CO2-Verdichter für Kraftfahrzeug-Klimaanlagen

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3160107B2 (ja) * 1993-02-23 2001-04-23 サンデン株式会社 斜板式可変容量圧縮機
DE19749727C2 (de) * 1997-11-11 2001-03-08 Obrist Engineering Gmbh Lusten Hubkolbenmaschine mit Schwenkscheibengetriebe
DE10010132C2 (de) * 2000-03-03 2003-12-11 Luk Fahrzeug Hydraulik Hubkolbenmaschine
AU2002213826A1 (en) * 2000-11-10 2002-05-21 Luk Fahrzeug-Hydraulik Gmbh And Co. Kg Reciprocating piston engine
JP2003120525A (ja) * 2001-10-19 2003-04-23 Sanden Corp 可変容量型圧縮機
KR100759423B1 (ko) * 2001-12-12 2007-09-17 한라공조주식회사 용량가변형 사판식 압축기
JP2003269328A (ja) * 2002-03-18 2003-09-25 Sanden Corp 可変容量圧縮機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1464836A2 (de) * 2003-04-04 2004-10-06 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter, insbesondere CO2-Verdichter für Kraftfahrzeug-Klimaanlagen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2005047697A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105114278A (zh) * 2015-07-24 2015-12-02 杭州绿聚科技有限公司 一种新型轴向柱塞泵

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Publication number Publication date
WO2005047697A1 (ja) 2005-05-26
JP2005146968A (ja) 2005-06-09
EP1693567A4 (de) 2007-10-24

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