WO2015176988A1 - Machine à pistons axiaux - Google Patents

Machine à pistons axiaux Download PDF

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Publication number
WO2015176988A1
WO2015176988A1 PCT/EP2015/060367 EP2015060367W WO2015176988A1 WO 2015176988 A1 WO2015176988 A1 WO 2015176988A1 EP 2015060367 W EP2015060367 W EP 2015060367W WO 2015176988 A1 WO2015176988 A1 WO 2015176988A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
axial piston
piston machine
bearing
machine according
Prior art date
Application number
PCT/EP2015/060367
Other languages
German (de)
English (en)
Inventor
Gert Baitinger
Christoph Beerens
Michael Kreisig
Markus LEUTERT
Rolf Müller
Berthold Repgen
Roland Schacherer
Falk Schneider
Peter Wieske
Original Assignee
Mahle International 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 Mahle International Gmbh filed Critical Mahle International Gmbh
Priority to DE112015002429.8T priority Critical patent/DE112015002429A5/de
Publication of WO2015176988A1 publication Critical patent/WO2015176988A1/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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F01B3/0017—Component parts, details, e.g. sealings, lubrication
    • 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
    • F04B27/109—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N31/00—Means for collecting, retaining, or draining-off lubricant in or on machines or apparatus

Definitions

  • the present invention relates to an axial piston machine with a shaft which is non-rotatably connected to a swash plate, according to the preamble of claim 1.
  • the invention also relates to a heat recovery system with such axial piston machine.
  • a generic axial piston machine with a shaft which is rotatably connected to a swash plate.
  • a plurality of cylinders are arranged, in each of which built and hollow pistons are arranged translationally adjustable.
  • Each of these pistons is coupled via an associated spherical bearing and a sliding block with the swash plate, whereby a movement of the respective piston causes a drive of the swash plate and thus a driving of the shaft.
  • each inlet opening of a cylinder is swept once over a control disk with an eccentrically arranged passage opening at each revolution and thereby supplied to the respective cylinder working fluid.
  • a cavity is provided around the shaft, which is delimited by the control disk, wherein the outlet openings belonging to the cylinders are guided through the cylinder head such that a temporary connection between the cavity and the expansion volume of the cylinder can be produced via the off-axis passage opening in the revolving control disk.
  • the efficiency should be able to be increased.
  • a piston machine with a housing in which a shaft is mounted in two pivot bearings.
  • at least one has an inner ring which sits without radial play on a bearing portion of a bearing portion of the shaft.
  • the axial length of the support portion corresponds to a central region of the bearing portion, wherein in both outer regions, a radial movement clearance between the outer regions and the inner ring is arranged.
  • an axial piston machine with a housing in which a shaft is rotatably mounted and represented by a sealing ring.
  • the sealing ring is arranged in an annular gap between the shaft and a housing wall and touched with its inner edge of the shaft.
  • an annular shoulder is arranged on the shaft axially opposite the inner side of the sealing ring.
  • a piston engine with a housing which encloses a housing interior, in which a drive shaft is rotatably mounted.
  • This drive shaft passes through a housing wall in a feedthrough hole and is mounted on this by a roller bearing and sealed by an outside of the rolling bearing arranged sealing ring.
  • the piston engine also has a partition, which is located between the sealing ring and the rolling element. is arranged bearing and a main space in which the rolling bearing is arranged, separated from an adjacent space which is sealed by the sealing ring separated.
  • a recirculation loop is provided between the main space and the subspace, which is formed separately from the inlet channel and the outlet channel. Via a conveyor while a flow is generated in the circulation.
  • the present invention addresses the problem of providing for an axial piston machine of the generic type an improved or at least one alternative embodiment, which is in particular easier to manufacture.
  • the present invention is based on the general idea, not for the first time a rotor of an axial piston machine in one piece or in one piece, but in a constructed manner.
  • at least one functional part is fixed on a shaft of the axial piston machine by means of a thermal joining method or by means of a press fit.
  • the axial piston according to the invention has in a known manner the rotor described above with the shaft which is rotatably connected to a disc. Cylindrical around and coaxial with this shaft cylinders are arranged, in which pistons are arranged translationally adjustable. Each cylinder is assigned an inlet opening.
  • the functional part is designed as a swash plate, as a valve body of a roller valve or as a bearing.
  • a swash plate as a valve body of a roller valve or as a bearing.
  • the shaft has a constant outer diameter or at least one functional portion on which an associated functional part can be fixed.
  • the shaft is equipped with a few functional sections, which did not differ in diameter.
  • previously required stops in the axial direction can be dispensed with and a positioning of the functional parts "free" on the shaft can be made possible.
  • fixation refer to the functional arranged reference surfaces arranged with which in the joining device, the position of the functional parts to the shaft, similar to a previously known cam assembly on a camshaft, is determined. Due to the constant outer diameter of the shaft, this can be formed, for example, as a drawn tube, whereby significantly higher quality requirements can be met, as was possible with cast shafts.
  • the shaft is connected via a magnetic coupling with a driven unit.
  • the axial piston machine is usually connected to the internal combustion engine via a corresponding ethanol-containing circuit with a heat exchanger.
  • the hot exhaust gases emitted from the internal combustion engine thereby generate the energy required for the evaporation of the ethanol so that it can expand in the cylinders and drive the axial piston engine.
  • the axial piston machine since such ethanol is highly flammable, the axial piston machine must be hermetically sealed in order to prevent inadvertent escape of the ethanol in any case.
  • the magnetic coupling according to the invention for example instead of a radial shaft sealing ring, an absolutely hermetic seal can be achieved without problems, since a transmission of the torque takes place exclusively due to magnetic fields.
  • Such a magnetic coupling also offers the great advantage that friction losses are eliminated, in particular in the region of a seal, which can mean a comparatively large loss of efficiency.
  • the magnetic coupling is designed as a gear, whereby a virtually arbitrary ratio of the rotational speed of the shaft to a subsequent coupled via the magnetic coupling driven unit is possible.
  • a collector in particular in the manner of a Schwannnns, a Fabricgestricks or a fleece is arranged on the swash plate, which separates from the ejected from the cylinders working fluid and collects oil.
  • an ethanol mixture is usually used, which is heated by combustion exhaust gases of the internal combustion engine via a heat exchanger and then expanded in the cylinders of the axial piston machine. After expansion, the ethanol mixture is expelled from the cylinders, this ethanol mixture containing aerosol entrained components.
  • These oil components are deposited, for example, upon impact on the swash plate and / or the shaft and collected on the inventively provided collector at a predefined location to further lubricating functions, for example, for a spherical bearing and / or a sliding block to be used.
  • the separated or collected by the collector oil can be thrown off, for example by the centrifugal force in the region of the spherical bearing or the sliding blocks, which can be lubricated reliably.
  • the collector is arranged, for example, so that the oil collected therein can be injected centrifugally due to the spherical bearing and / or the sliding block.
  • the swash plate has an oblique oil passage through which the separated and collected by the collector oil can reach the bottom of the swash plate and can be injected from there in the direction of the spherical bearing and / or the sliding block.
  • the oblique oil passage thus a two-sided lubrication of the spherical bearing or the sliding blocks is possible.
  • the outlet of the oil passage at the bottom of the swash plate is located radially outside of the inlet at the top, so that the oil passage is caused due to centrifugal forces.
  • an oil guide channel is provided in the shaft, which leads from the collector to a bearing and / or to a labyrinth seal of the shaft on the housing.
  • An intake of the oil collected in the collector through the oil guide channel can be carried out, for example, either by the principle of a water jet pump through a small amount of high pressure gas flowed through or by a conveying action of a arranged in a sealing region labyrinth seal.
  • the labyrinth seal promotes from the smaller diameter to the larger diameter, or through the radial sealing gaps by a centrifugal effect, the required oil.
  • the labyrinth seal itself also has the task of protecting the actual radial shaft seal from pressure surges and also serves as a seal to the pressure chamber.
  • the shaft is mounted on at least one designed as a rolling bearing fixed bearing, wherein the fixed bearing is designed as an employee ball bearings.
  • a rolling bearing may for example have two adjacent ball bearings, wherein the inner rings are each mounted by a press fit on the shaft.
  • An axial support on the housing takes place via an outer ring of the first ball bearing.
  • the inner ring of the second ball bearing is still pressed after the installation of the shaft in the housing, whereby an axial clearance can be eliminated and without complex screwing, balancing elements or disc springs, which would otherwise be required to to eliminate unwanted axial play.
  • such an axial clearance causes an undesirable tolerance in the respective pistons, and thus a harmful volume, which also adversely affects the efficiency.
  • the collector is designed such that separated oil is centrifugally thrown off only in those areas in which there are a spherical bearing and / or a sliding block.
  • the collector has or is formed by a depression in the swash plate, which is partially flattened in the direction of the sliding blocks and / or the spherical bearings and thereby opened.
  • the collector may also include a ring which is partially open in the direction of the sliding blocks and / or the spherical bearings to spin off separated oil.
  • the ring has an opening which is arranged in the radial direction in alignment with the spherical bearing. A centrifugally induced leakage of separated oil from the ring can thus take place exclusively through the opening.
  • This ring may be formed, for example, as a metal ring or a plastic ring.
  • FIG. 1 is a sectional view through an axial piston machine according to the invention with a built shaft and magnetic coupling
  • FIG. 2 is a view as in Figure 1, but without magnetic coupling and with oil guide channel in the shaft,
  • Fig. 3 a sectional view through a swash plate with a collector having a trough
  • Fig. 4 is a view as in Fig. 3, but with a collector with a
  • an axial piston machine 1 which may for example be part of a heat recovery system 2 of a motor vehicle, not shown in more detail, has a rotor 37 with a shaft 3 which is connected in a rotationally fixed manner to a swash plate 4.
  • a rotor 37 Arranged around the shaft 3 and coaxially therewith are preferably at least four cylinders 5, in which built and hollow pistons 6 are arranged so as to be translationally adjustable.
  • Each of these pistons 6 is coupled via a spherical bearing 7 and a sliding block 8 with the swash plate 4 for driving the shaft 3.
  • Each cylinder 5 is also assigned an inlet opening 9.
  • the axial piston machine 1 in this case has a control disk 10 which covers the respective inlet opening 9 and has an eccentrically arranged passage opening 11.
  • the control disk 10 is rotatably connected to the shaft 3. at each revolution of the control disk 10 passes through the passage opening 1 1 each time each inlet opening 9 and thereby allows access of working fluid in the associated cylinder 5.
  • the working medium in particular an ethanol mixture is previously collected in a collecting space 12 under pressure, said collecting space 12th
  • said collecting space 12th can be connected via a heat exchanger with an exhaust line of an internal combustion engine heat transfer. In the collecting space 12, the heated by the exhaust heat of the exhaust line and pressurized ethanol mixture is collected before it is directed to the expansion and thus to drive the axial piston machine 1 in the respective cylinder 5.
  • the rotor 37 is now designed as a constructed rotor 37 in the axial piston machines 1 shown in FIGS. 1 and 2, wherein at least one functional part 13 is fixed on the shaft 3 by means of thermal joining methods or by means of a press fit.
  • the advantage of a built rotor 37 is clearly apparent, since now no longer the entire rotor 37, ie the shaft 3 and the functional parts 13, for example, the swash plate 4, a bearing 14, 28, a control disk 10 or a valve body 15 are made together but individually and therefore much easier. In particular, there is no need for elaborate reworking, which was absolutely necessary in the previous wave with integrally formed functional parts.
  • the functional parts 13, ie for example the swashplate 4, the valve body 15 of the roller slide valve and / or the bearings 14, 28 are preferably fixed on the shaft 3 via a thermal press fit, but alternatively also via a longitudinal or transverse press fit.
  • the shaft 3 preferably has a constant outer diameter and can be designed, in particular, as a drawn tube and thus of the highest quality that can be produced.
  • the shaft 3 has at least one functional portion 16 on which an associated functional part 13, ie, for example, the swash plate 4 or the control disk 10, can be fixed.
  • the shaft 3 is formed as a continuous tube with some functional sections 16, which, however, do not differ in their diameter.
  • the shaft 3, that is, the rotor 37 is connected via a magnetic coupling 17 to a driven unit 18.
  • a magnetic coupling 17 can be used, for example, instead of a radial shaft sealing ring 19 (see FIG. 2) which is usually used in this area and allows a hermetic sealing of the axial piston machine 1 to the outside, whereby in particular unwanted leakage of the easily inflammable ethanol mixture can be reliably avoided can.
  • friction losses in the region of a seal for example a labyrinth seal 20, so that a particularly easy mounting of the shaft 3 can be achieved omitted.
  • the magnetic coupling 17 may also be designed as a transmission, in particular as a magnetic transmission, and allow a translation of the speed.
  • the magnetic coupling 17 can also serve from the output side in the case of entrainment of the axial piston 1 by the output, for example by a mechanical coupling with the drive train of a truck or a car as overload clutch to avoid damage.
  • Such an overload clutch which is designed as a magnetic coupling 17, causes slippage, provided that the torque exceeds the magnetic forces required in the magnetic coupling 17.
  • iron rods 21 may be provided, with which the translation effect can be realized.
  • a sealing sleeve 23 is arranged, which enables the hermetic sealing of the axial piston machine 1.
  • the torque transmission from the shaft 3 to the drive rotor 22 takes place via a feather key 24.
  • a collector 25 in particular in the manner of a sponge or a fleece, is arranged, which serves for collecting oil.
  • This oil is initially entrained in the ethanol mixture aerosol and ejected from the cylinders 5 after the power stroke.
  • the oil-mist-containing ethanol mixture When the oil-mist-containing ethanol mixture is ejected, it either bounces against a baffle plate (not shown), against the swash plate 4 and / or onto the shaft 3, whereby the oil contained in the ethanol mixture aerosol is separated off. Subsequently, this is due to gravity or centrifugal force in the direction of the collector 25 and is collected there. In this way, the formation of a lubricant reservoir can be achieved, with centrifugal force can be sprayed from this oil or lubricant to the spherical bearing 7 and / or the sliding block 8 and lubricates this.
  • the swash plate 4 penetrating an oblique oil passage 26 is provided, through which separated oil from the collector 25 to the bottom of the
  • Swash plate 4 reach and from there also centrifugal force in the direction of the spherical bearing 7 and / or the sliding block 8 can be injected.
  • an oil guide channel 27 may be provided which leads from the collector 25 to a bearing 14, 28, 28 'and / or to the labyrinth seal 20 of the shaft 3 on the housing 29.
  • the subsidized in the oil guide channel 27 Lubricant ström or oil flow can be done either by the principle of a water jet pump through a small amount of high-pressure gas flow through or by a conveying action of a arranged in the sealing region labyrinth seal 20.
  • the labyrinth seal 20 serves to protect the radial shaft seal 19 from pressure surges and also serves as a seal of the axial piston machine first About the radial arranged in the region of the labyrinth seal 20 portions of the oil guide channel 27 lubricating oil is sucked from the collector 25, wherein the suction effect is generated by the stepped labyrinth seal 20.
  • the labyrinth seal 20 thereby promotes the smaller diameter to the larger diameter or by the radial sealing gaps due to the centrifugal effect acting there. By sucking lubricating oil from the collector 25, the radial shaft seal 19 lubricated and derived in this heat can be derived.
  • a part of the labyrinth seal 20 is formed by the shaft 3 itself, which is tapered in the region of the opening through the housing 29 step-like.
  • the shaft 3 itself is also mounted on at least one designed as a roller bearing fixed bearing 28 ', wherein the fixed bearing 28' is formed as an employed ball bearing.
  • the fixed bearing 28 ' according to the figure 1 in this case has two ball bearings arranged adjacent to each other, each with an outer ring 31, 31' and an inner ring 32, 32 '.
  • the bearing 14 may be lubricated, placing it outside the flow region and thereby ideally with respect to lubrication.
  • the bearing 14 is outside the high-pressure region, which is given for example in the plenum 12.
  • Further storage of the shaft 3 can be carried out, for example, in at least one movable bearing designed as a sliding bearing 36 in the radial direction, wherein the floating bearing 36, in particular its sliding body may have a polymer coating, in particular a polymer with a PTFE content.
  • the sliding properties can be improved and a frictional resistance can be reduced.
  • the collector 25 is designed such that separated oil is centrifugally driven only in the areas in which a spherical bearing 7 is produced and / or a sliding block 8 is located. This can be achieved, for example, by the two alternatives described below.
  • the collector 25 has a recess 38 in the swash plate 4 or is formed by it, which is partially flattened in the direction of the sliding blocks 8 and / or the spherical bearing 7 and thereby opened to spin off separated oil.
  • the flattened edge 39 is provided on the left side, whereas on the right side, an undercut-like edge 40 is provided which prevents ejection of separated oil.
  • the ring 41 which may be formed as a sheet metal ring or as a plastic ring, an opening 42 which is arranged in the radial direction in alignment with the spherical bearing 7. A centrifugally induced discharge of separated oil from the ring 41 can thus take place exclusively via the opening 42.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une machine à pistons axiaux (1), comprenant - un rotor (37) pourvu d'un arbre (3) qui est lié solidairement en rotation à un plateau oscillant (4), - des cylindres (5) qui sont disposés annulairement autour de l'arbre (3) et coaxialement à celui-ci et dans lesquels des pistons (6) sont disposés de façon déplaçable en translation, - un orifice d'entrée (9) est associé à chaque cylindre (5). L'invention est caractérisée en ce que le rotor (37) est conçu comme un rotor intégré, au moins un élément fonctionnel (13) étant fixé sur l'arbre (3) au moyen de procédés d'assemblage thermique ou par ajustage serré.
PCT/EP2015/060367 2014-05-23 2015-05-11 Machine à pistons axiaux WO2015176988A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112015002429.8T DE112015002429A5 (de) 2014-05-23 2015-05-11 Axialkolbenmaschine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014209894.7A DE102014209894A1 (de) 2014-05-23 2014-05-23 Axialkolbenmaschine
DE102014209894.7 2014-05-23

Publications (1)

Publication Number Publication Date
WO2015176988A1 true WO2015176988A1 (fr) 2015-11-26

Family

ID=53189798

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/060367 WO2015176988A1 (fr) 2014-05-23 2015-05-11 Machine à pistons axiaux

Country Status (2)

Country Link
DE (2) DE102014209894A1 (fr)
WO (1) WO2015176988A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015225292A1 (de) * 2015-12-15 2017-06-22 Mahle International Gmbh Axialkolbenmaschine
EP4023860B1 (fr) 2021-01-04 2023-08-23 Volvo Car Corporation Système d'évaseur

Citations (13)

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JPH0533761A (ja) * 1991-07-31 1993-02-09 Toyota Autom Loom Works Ltd 斜板式圧縮機における斜板支持構造
DE4412570A1 (de) * 1993-04-14 1994-10-20 Toyoda Automatic Loom Works Kompressor mit Detektoreinrichtungen für eine Drehbewegung
DE19820296A1 (de) * 1997-05-13 1999-02-11 Zexel Corp Taumelscheibenverdichter
DE19852246A1 (de) 1998-11-12 2000-05-25 Brueninghaus Hydromatik Gmbh Hydraulische Maschine mit einem Gehäuse und einer mit einem Dichtring abgedichteten Welle
EP1167761A2 (fr) * 2000-06-27 2002-01-02 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau en biais
EP1262662A1 (fr) * 2001-05-21 2002-12-04 Kabushiki Kaisha Toyota Jidoshokki compresseur du type à plateau oscillant
DE19902518C2 (de) 1999-01-22 2003-04-10 Brueninghaus Hydromatik Gmbh Hydraulische Maschine, insbesondere Kolbenmaschine, mit einem Gehäuse und einer darin angeordneten Trennwand
EP1426617A2 (fr) * 2002-12-05 2004-06-09 Kabushiki Kaisha Toyota Jidoshokki Procédé pour ajuster le jeu dans une machine rotative
DE10360003A1 (de) 2003-12-19 2005-07-14 Brueninghaus Hydromatik Gmbh Kolbenmaschine, Welle und Wälzlager für eine Kolbenmaschine
WO2006066831A1 (fr) * 2004-12-20 2006-06-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Compresseur a plateau oscillant fonctionnant a sec, comportant un plateau oscillant monte sur roulement
DE102006025370A1 (de) * 2005-06-02 2007-01-11 Denso Corp., Kariya Kompressor und Konstantgeschwindigkeitsgelenk bzw. Doppelgelenk
EP2045467A2 (fr) * 2007-10-03 2009-04-08 Kabushiki Kaisha Toyota Jidoshokki Compresseur de type brise-flot à capacité variable
DE102011118622A1 (de) 2011-11-16 2013-05-16 Amovis Gmbh Axialkolbenmaschine mit Auslasssteuerung

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US1714145A (en) * 1922-11-14 1929-05-21 Sperry Dev Co Crankless engine
DE1293783B (de) * 1962-09-10 1969-04-30 Papst Hermann Taumelscheiben-Triebwerk fuer Kolben-Brennkraftmaschinen
US6112639A (en) * 1995-12-18 2000-09-05 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Structure for collecting leaking oil in compressor
JPH10196515A (ja) * 1997-01-16 1998-07-31 Toyota Autom Loom Works Ltd 流体機械における駆動シャフトと回転要素の圧入嵌合構造
JPH10213062A (ja) * 1997-01-31 1998-08-11 Zexel Corp 可変容量型斜板式圧縮機
DE102010046249A1 (de) * 2010-09-22 2012-03-22 Robert Bosch Gmbh Hydraulische Kolbenmaschine
DE102010052508A1 (de) * 2010-11-26 2012-05-31 Daimler Ag Abwärmenutzungsvorrichtung
DE102011118503A1 (de) * 2011-11-15 2013-05-16 Robert Bosch Gmbh Druckgekapseltes Pumpengehäuse

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0533761A (ja) * 1991-07-31 1993-02-09 Toyota Autom Loom Works Ltd 斜板式圧縮機における斜板支持構造
DE4412570A1 (de) * 1993-04-14 1994-10-20 Toyoda Automatic Loom Works Kompressor mit Detektoreinrichtungen für eine Drehbewegung
DE19820296A1 (de) * 1997-05-13 1999-02-11 Zexel Corp Taumelscheibenverdichter
DE19852246A1 (de) 1998-11-12 2000-05-25 Brueninghaus Hydromatik Gmbh Hydraulische Maschine mit einem Gehäuse und einer mit einem Dichtring abgedichteten Welle
DE19902518C2 (de) 1999-01-22 2003-04-10 Brueninghaus Hydromatik Gmbh Hydraulische Maschine, insbesondere Kolbenmaschine, mit einem Gehäuse und einer darin angeordneten Trennwand
EP1167761A2 (fr) * 2000-06-27 2002-01-02 Kabushiki Kaisha Toyota Jidoshokki Compresseur à plateau en biais
EP1262662A1 (fr) * 2001-05-21 2002-12-04 Kabushiki Kaisha Toyota Jidoshokki compresseur du type à plateau oscillant
EP1426617A2 (fr) * 2002-12-05 2004-06-09 Kabushiki Kaisha Toyota Jidoshokki Procédé pour ajuster le jeu dans une machine rotative
DE10360003A1 (de) 2003-12-19 2005-07-14 Brueninghaus Hydromatik Gmbh Kolbenmaschine, Welle und Wälzlager für eine Kolbenmaschine
WO2006066831A1 (fr) * 2004-12-20 2006-06-29 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Compresseur a plateau oscillant fonctionnant a sec, comportant un plateau oscillant monte sur roulement
DE102006025370A1 (de) * 2005-06-02 2007-01-11 Denso Corp., Kariya Kompressor und Konstantgeschwindigkeitsgelenk bzw. Doppelgelenk
EP2045467A2 (fr) * 2007-10-03 2009-04-08 Kabushiki Kaisha Toyota Jidoshokki Compresseur de type brise-flot à capacité variable
DE102011118622A1 (de) 2011-11-16 2013-05-16 Amovis Gmbh Axialkolbenmaschine mit Auslasssteuerung

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Publication number Publication date
DE102014209894A1 (de) 2015-11-26
DE112015002429A5 (de) 2017-03-16

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