EP1218639B1 - Compresseur a piston axial - Google Patents

Compresseur a piston axial Download PDF

Info

Publication number
EP1218639B1
EP1218639B1 EP00969409A EP00969409A EP1218639B1 EP 1218639 B1 EP1218639 B1 EP 1218639B1 EP 00969409 A EP00969409 A EP 00969409A EP 00969409 A EP00969409 A EP 00969409A EP 1218639 B1 EP1218639 B1 EP 1218639B1
Authority
EP
European Patent Office
Prior art keywords
plate
drive shaft
piston
disc
sliding blocks
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.)
Expired - Lifetime
Application number
EP00969409A
Other languages
German (de)
English (en)
Other versions
EP1218639A1 (fr
Inventor
Otfried 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
Application filed by Zexel Valeo Compressor Europe GmbH filed Critical Zexel Valeo Compressor Europe GmbH
Publication of EP1218639A1 publication Critical patent/EP1218639A1/fr
Application granted granted Critical
Publication of EP1218639B1 publication Critical patent/EP1218639B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B27/10—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 invention relates to an axial piston compressor, such as For example, from JP4-148083A can be seen with a drive shaft, a Disc which is mounted on the drive shaft so that they are relative to this um a pivot axis can be displaced, and at least one piston, the provided with sliding blocks which slide on a track on the disc.
  • Such an axial piston compressor can in particular in an air conditioner for Motor vehicles are used. It serves to make a refrigerant out of one Heat exchanger, in which it evaporates under heat absorption to suck and to compress to a higher pressure, so that it in another Heat exchanger the heat at a higher temperature level again can deliver. Subsequently, the refrigerant undergoes expansion in an organ a throttling to the pressure level of the first heat exchanger.
  • each piston is caused by the interaction of connected to the piston sliding blocks with the disc, relative to the Drive shaft is pivotable. If the disc is not relative to the drive shaft is pivoted, so the central axis of the disc with the longitudinal axis of the Drive shaft coincides, there is no stroke, since the distance between for example, the bottom of the cylinder in which the piston is arranged, and the tread does not change during one revolution of the drive shaft. In contrast, when the disc is pivoted so that the central axis of the disc with the longitudinal axis of the drive shaft a non-zero angle which is usually 20 ° or less, the distance changes between the tread of the disc and the bottom of the cylinder at each Rotation of the drive shaft periodically between a minimum value and a Maximum value. The piston coupled to the disk is thus then if the distance is minimal, in its top dead center, that is maximum in the Cylinder pushed in while he is at maximum distance in his bottom dead center is located.
  • the track of the sliding blocks attached to the piston on the disc changes depending on the tilt angle of the disc.
  • the pivoting disc is so measured that when not pivoted disc only a very small edge between the raceway of the sliding blocks and the outer edge of the disc remains. It follows that with pivoted disc, the career of the Sliders in the areas of the disc, the upper and the lower Dead center correspond to the piston, goes beyond the edge of the disc. This is a consequence of the apparent shortening of the disc during pivoting. Due to the fact that the track in the pivoted state of the disc beyond its edge, results in a reduced area, the Transferring the forces between the disc and the sliding blocks stands.
  • the maximum force between the sliding blocks and the .Screen acts.
  • the coincidence of reducing power transmission available area on the one hand with the maximum of transferring force on the other hand leads to an increase in the surface pressure between the disc and the raceway, which in extreme cases to a feeding between the sliding block and the disc can lead.
  • the object of the invention is therefore to provide an axial piston compressor to improve the above-mentioned type such that a seizure between the sliding blocks and the disc under all operating conditions reliable is prevented.
  • an axial piston compressor according to the invention with the features of Characteristic part of claim 1 is due to the offset between the median plane of the disc and the pivot axis of the disc rotational movement of the disc superimposed on a translational movement. This causes the disc relative to the sliding blocks whose position is predetermined, shifts when panning. This shift can be targeted be used to the emergence of the career of the sliding blocks on the Either to eliminate the edge of the disc completely or to reduce significantly. This eliminates or reduces the increase in surface pressure between sliding blocks and career.
  • the pivot axis of the disc with respect to the Center plane of the disc on the piston side facing.
  • this Design will reduce the overlap between the sliding blocks and the disc by pivoting the disc in the area counteracted, which corresponds to the top dead center of the respective piston, So in the operating point in which the force acting on the piston on biggest one is.
  • the resulting in this design reduction of Overlap between the sliding block and the track of the disc, which is twice as large is like in a design according to the prior art with a Pivot axis, which coincides with the median plane of the disc can to be tolerated, since at the appropriate time on the piston acting force is relatively low.
  • Which, despite the reduction of Contact surface between the sliding blocks and the raceway of the disc resulting surface pressure is below the critical values.
  • the disc is a Swash plate, which can be rotated by the drive shaft and whose pivot angle can be adjusted with respect to the drive shaft.
  • a Swash plate which can be rotated by the drive shaft and whose pivot angle can be adjusted with respect to the drive shaft.
  • the Disk is a swash plate, which is rotatably mounted on a swash plate is and whose pivot angle with respect to the drive shaft that of Swash plate corresponds.
  • This type apart from the translational Movement of the swash plate, the rotation of the pivoting movement is superimposed, corresponds to a type, as for example from the DE 196 21 174 A1, combines the advantage of a targeted reduction the surface pressure with the inherent advantage of this type of a particular low-friction operation.
  • an inventive Axial piston compressor is provided that at a distance between the Longitudinal axis of the drive shaft and the longitudinal axis of the piston of 30 mm, a diameter of the voltage applied to the track plane surface of the sliding blocks of 8 mm and a maximum swing angle between the longitudinal axis of the Drive shaft and the center axis of the disc of 18 ° the distance between the Center plane of the disc and the pivot axis of the disc is about 1 mm.
  • the disc is the disc when pivoting relative to the track of the Sliders moved only so far that on one side of the disc a Reduction of the overhang of the track over the outer edge of the disc results; the theoretically possible displacement of the disc so far that the Run completely in the area of a dead center of the piston again the disc is deliberately not sought, since with increasing offset between the pivot axis and the median plane of the disc and the Mass center of the disc relative to the longitudinal axis of the drive shaft emigrates.
  • the specified value represents at the mentioned geometric A good compromise between a reduction in Surface pressure on the one hand and increasing the imbalance of the disc on the other hand.
  • FIG. 1 shows an axial piston compressor according to the prior art.
  • This contains a housing 10, in which rotatably a drive shaft 12th is stored.
  • a swash plate 14th With the drive shaft 12 is rotatably a swash plate 14th connected, which is pivotally mounted about a pivot axis C.
  • the Pivot axis C intersects the longitudinal axis L of the drive shaft 12 in the right Angle.
  • the swash plate 14 can about the pivot axis C between a Position in which the pivot angle between the median plane M of Swash plate 14 and a plane perpendicular to the longitudinal axis L of the drive shaft is about zero, and pivoted to a maximum pivoted position, in the swing angle ⁇ is about 20 °.
  • the way the adjustment the swash plate 14 is achieved and controlled is, on the one hand well known and second, not relevant to the understanding of the invention, so that thereon will not be received.
  • each piston 18th In the housing a plurality of cylinders 16 are formed, in each of which a piston 18th are slidably mounted.
  • the longitudinal axis Z of each piston and each Cylinder is aligned parallel to the longitudinal axis L of the drive shaft.
  • the Compressor can be equipped with up to seven such pistons in the uniform angular distance around the drive shaft are arranged around.
  • Each piston is provided with two sliding blocks 20, each having a circular Planar surface 22 and a spherical section-shaped pivot surface 24 have.
  • the pivot surface of each slider 20 is in a correspondingly shaped Receiving surface 26 received on the piston so that the swash plate 14th between the mutually facing and parallel aligned planar surfaces 22nd the two sliding blocks of a piston is added. This way, when the swash plate 14 to a non-zero pivot angle ⁇ is pivoted, the tumbling rotational movement of the swash plate in one translational movement of the piston 18 implemented.
  • the plane surfaces are running 22 of the sliding blocks 20 on tracks on the swash plate 14, which coincides with the Change swivel angle ⁇ .
  • the swash plate 14 When the center axis of the swash plate 14 with the Longitudinal axis L of the drive shaft 12 coincides, the swash plate 14 itself that extends perpendicular to the drive shaft 12, resulting in a circular Track of the sliding blocks 20 on the swash plate 14.
  • the radius of this Career corresponds to the distance between the center of the of the Receiving surfaces 26 defined ball joint of each cylinder and the Longitudinal axis L. Since in the illustrated embodiment, the center of each Ball joint is located on the longitudinal axis Z of each cylinder 16, corresponds to the Radius of the track the distance between the longitudinal axis Z and the Longitudinal axis L.
  • the course of the force F acting on the piston is shown as a function of the angle of rotation ⁇ of the swash plate 14.
  • the piston is initially accelerated in the direction of bottom dead center, while at the same time refrigerant is drawn in. For this reason, the forces acting on the piston are negative in some areas.
  • FIG. 6 is schematically the invention Design shown.
  • the pivot axis C by a dimension V to the Center plane of the swash plate 14 offset.
  • the offset V is chosen here, that the pivot axis C on the side of the (not shown in Figure 6) piston lying, which are driven by the swash plate 14. Due to the offset V results when pivoting the swash plate 14 in addition to rotational movement a translational movement. As a result, the Outer edge of the swash plate 14, considered for the positions corresponding to the Dead centers of the pistons, arranged eccentrically.
  • the sliding block Due to the reduction of surface pressure between the sliding blocks and the swashplate at maximum load, the sliding block may with smaller dimensions are executed. This allows for a more compact Design. Since the flat surface 22 of the sliding blocks 20 no longer at maximum load beyond the edge of the swash plate 14, voltage spikes and thus reducing wear due to edge pressure. Due to the enlarged Supernatant a of the plane surface 22 in the region of the bottom dead center results improved wetting of the flat surface of the sliding blocks by the oil mist in the Interior of the housing 10th
  • Swivel axis C results in pivoted swash plate 14 that the Center of gravity of the swash plate eccentric with respect to the longitudinal axis L the drive shaft is arranged. This results tend to be low Imbalances in the operation of the compressor. As these imbalances increase with Offset V increase, can be provided as a compromise, not the total overhang a in the area of top dead center to compensate but only so far that the surface pressure only to a harmless degree increases.

Landscapes

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

Claims (4)

  1. Compresseur à pistons axiaux avec un arbre d'entraínement (12), un disque (14) logé de telle manière sur l'arbre d'entraínement qu'il puisse pivoter par rapport à l'arbre d'entraínement autour d'un axe de pivotement (C) et au moins un piston (18), la position de l'axe de pivotement (C) du disque (14) étant excentrée par rapport au plan médian du disque,
       caractérisé en ce que le piston (18) est muni d'au moins deux éléments coulissants (20) qui coulissent sur le disque (14) selon une trajectoire de glissement, alors que le piston (18) entoure les éléments coulissants (20) en forme de C, et en ce que, pour déplacer le disque (14) par rapport aux éléments coulissants (20) de telle façon que la trajectoire de glissement des éléments coulissants (20) ne soit pas ou seulement faiblement en dépassement au-delà du bord du disque, l'axe de pivotement (C) du disque (14) se trouve, en tant que partie d'une articulation logée avec une possibilité de déplacement longitudinal sur l'arbre d'entraínement, sur l'axe longitudinal (L) de l'arbre d'entraínement (12) et, par rapport au plan médian du disque, sur le côté dirigé vers le piston (18).
  2. Compresseur à pistons axiaux selon la revendication 1, caractérisé en ce que le disque est un disque placé en biais (14) qui peut être mis en rotation par l'arbre d'entraínement (12) et dont l'angle de pivotement (α) peut faire l'objet d'un réglage par rapport à l'arbre d'entraínement.
  3. Compresseur à pistons axiaux selon la revendication 1 ou 2, caractérisé en ce que le disque est un disque animé d'un mouvement de balancement qui est disposé de manière à pouvoir tourner sur un disque placé en biais et dont l'angle de pivotement par rapport à l'arbre d'entraínement correspond à celui du disque placé en biais.
  4. Compresseur à pistons axiaux selon l'une quelconque des revendications précédentes, caractérisé en ce qu'avec un espacement entre l'axe longitudinal (L) de l'arbre d'entraínement et l'axe longitudinal (Z) des pistons de 30 mm, un diamètre de la surface plane (22) des éléments coulissants (20) s'appuyant la trajectoire de glissement de 8 mm et un angle de pivotement maximal (α) entre l'axe longitudinal de l'arbre d'entraínement et l'axe médian du disque de 18°, l'espacement entre le plan médian du disque et l'axe de pivotement du disque (14) n'est pas plus grand qu'environ 1 mm.
EP00969409A 1999-10-04 2000-10-04 Compresseur a piston axial Expired - Lifetime EP1218639B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19947677A DE19947677B4 (de) 1999-10-04 1999-10-04 Axialkolbenverdichter
DE19947677 1999-10-04
PCT/EP2000/009705 WO2001025635A1 (fr) 1999-10-04 2000-10-04 Compresseur a piston axial

Publications (2)

Publication Number Publication Date
EP1218639A1 EP1218639A1 (fr) 2002-07-03
EP1218639B1 true EP1218639B1 (fr) 2005-06-01

Family

ID=7924382

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00969409A Expired - Lifetime EP1218639B1 (fr) 1999-10-04 2000-10-04 Compresseur a piston axial

Country Status (5)

Country Link
US (1) US6766726B1 (fr)
EP (1) EP1218639B1 (fr)
AU (1) AU7913700A (fr)
DE (2) DE19947677B4 (fr)
WO (1) WO2001025635A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004027862A (ja) * 2002-06-21 2004-01-29 Honda Motor Co Ltd 膨張機
US8900069B2 (en) 2010-12-28 2014-12-02 Taylor Made Golf Company, Inc. Fairway wood center of gravity projection
US8235844B2 (en) 2010-06-01 2012-08-07 Adams Golf Ip, Lp Hollow golf club head
US7753806B2 (en) 2007-12-31 2010-07-13 Taylor Made Golf Company, Inc. Golf club
US8196506B2 (en) * 2009-08-17 2012-06-12 Delphi Technologies, Inc. Variable stroke compressor design
US9089749B2 (en) 2010-06-01 2015-07-28 Taylor Made Golf Company, Inc. Golf club head having a shielded stress reducing feature
US8827831B2 (en) 2010-06-01 2014-09-09 Taylor Made Golf Company, Inc. Golf club head having a stress reducing feature
US8821312B2 (en) 2010-06-01 2014-09-02 Taylor Made Golf Company, Inc. Golf club head having a stress reducing feature with aperture

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3416638A1 (de) * 1984-05-05 1985-11-14 Diesel Kiki Co. Ltd., Tokio/Tokyo Taumelscheiben-kolbenpumpe
US4674957A (en) 1984-12-22 1987-06-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control mechanism for variable displacement swash plate type compressor
JPH0697034B2 (ja) * 1988-06-07 1994-11-30 松下電器産業株式会社 可動斜板式コンプレッサ
JPH04143469A (ja) * 1990-10-03 1992-05-18 Zexel Corp ワブルプレート型コンプレッサの回転バランス調節装置
JP2846096B2 (ja) * 1990-10-10 1999-01-13 株式会社日本自動車部品総合研究所 可変容量式斜板型圧縮機
JPH0968162A (ja) * 1995-06-20 1997-03-11 Toyota Autom Loom Works Ltd 容量可変型斜板式圧縮機
JP3733633B2 (ja) * 1996-02-01 2006-01-11 株式会社豊田自動織機 可変容量圧縮機
DE19621174A1 (de) * 1996-05-24 1997-11-27 Danfoss As Kompressor, insbesondere für Fahrzeug-Klimaanlagen

Also Published As

Publication number Publication date
US6766726B1 (en) 2004-07-27
DE19947677B4 (de) 2005-09-22
EP1218639A1 (fr) 2002-07-03
DE50010473D1 (de) 2005-07-07
WO2001025635A1 (fr) 2001-04-12
DE19947677A1 (de) 2001-04-19
AU7913700A (en) 2001-05-10

Similar Documents

Publication Publication Date Title
DE3609796C2 (fr)
DE4290951C1 (de) Taumelscheiben-Kompressor mit veränderlicher Leistung
DE4229069C2 (de) Taumelscheiben-Kältemittelkompressor für ein Kühlsystem
DE69407226T2 (de) Lageranordnung zur Verwendung in einem Kompressor
DE69731340T2 (de) Kompressor mit variabler Fördermenge
DE69604972T2 (de) Taumelscheibenkompressor mit veränderlicher Förderleistung und mit einer verbesserten Gelenkvorrichtung zur Neigungsunterstützung einer Taumelscheibe
EP1607630A1 (fr) Compresseur à piston
WO2014187512A1 (fr) Pompe à pistons axiaux de type à plateau inclinable
DE69621308T2 (de) Schiefscheibenverdichter mit veränderlicher Verdrängung
DE3500298C2 (fr)
DE19530210C2 (de) Taumelscheibenverdichter
DE4210083A1 (de) Einkopfkolben-schraegscheibenkompressor veraenderlicher leistung mit einrichtungen zur verhinderung des kolbenantriebs
EP1218639B1 (fr) Compresseur a piston axial
DE19754440A1 (de) Verdichter vom Einkopfkolben-Typ
DE19712348C2 (de) Taumelscheibenkompressor mit einfach-wirkenden Kolben
WO2006081966A1 (fr) Compresseur a pistons axiaux
DE19621174A1 (de) Kompressor, insbesondere für Fahrzeug-Klimaanlagen
DE3788176T2 (de) Schiefscheibenverdichter mit veränderlicher Verdrängung.
DE10152097B4 (de) Verstellbarer Taumelscheibenkompressor
DE69938209T2 (de) Kolbenführung für einen Taumelscheibenkompressor
EP1387957B1 (fr) Machine a pistons elevateurs dotee d'une articulation
DE69723556T2 (de) Taumelscheibenlagerung für einen kompressor mit variabler verdrängung
EP1718867B1 (fr) Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile
DE19515658A1 (de) Taumelscheibenkompressor mit schwenkbarer Taumelscheibe
DE10051420A1 (de) Zylinderblock eines Axialkolbenverdichters mit verlängerter Zylinderlauffläche

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: 20020327

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17Q First examination report despatched

Effective date: 20040405

RBV Designated contracting states (corrected)

Designated state(s): AT BE DE FR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ZEXEL VALEO COMPRESSOR EUROPE GMBH

RBV Designated contracting states (corrected)

Designated state(s): DE FR

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR

REF Corresponds to:

Ref document number: 50010473

Country of ref document: DE

Date of ref document: 20050707

Kind code of ref document: P

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20051230

Year of fee payment: 6

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: VALEO COMPRESSOR EUROPE GMBH

26N No opposition filed

Effective date: 20060302

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070501

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20081028

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091102