US20100000401A1 - Axial-piston machine having an antiwear layer - Google Patents

Axial-piston machine having an antiwear layer Download PDF

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Publication number
US20100000401A1
US20100000401A1 US11/632,094 US63209405A US2010000401A1 US 20100000401 A1 US20100000401 A1 US 20100000401A1 US 63209405 A US63209405 A US 63209405A US 2010000401 A1 US2010000401 A1 US 2010000401A1
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US
United States
Prior art keywords
layer
piston machine
sliding
sliding side
axial piston
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.)
Abandoned
Application number
US11/632,094
Other languages
English (en)
Inventor
Thomas Beck
Alexander Schattke
Sasha Henke
Bernd Emrich
Georg Jacobs
Herbert Kutrz
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.)
Robert Bosch GmbH
Brueninghaus Hydromatik GmbH
Original Assignee
Robert Bosch GmbH
Brueninghaus Hydromatik 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 Robert Bosch GmbH, Brueninghaus Hydromatik GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JACOBS, GEORG, KURZ, HERBERT, EMRICH, BERN, HENKE, SASCHA, SCHATTKE, ALEXANDER, BECK, THOMAS
Publication of US20100000401A1 publication Critical patent/US20100000401A1/en
Abandoned 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/08—Ceramics; Oxides
    • F05C2203/0804—Non-oxide ceramics
    • F05C2203/0808—Carbon, e.g. graphite
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the present invention relates to a hydrostatic machine configured as axial-piston machine.
  • German Patent Application Serial No. DE 102 23 844 A1 Situated on one side of the paired surfaces rubbing against each other is a plastic layer, and on the other side is a carbon-containing layer.
  • the regions of the surfaces of the control plate and the cylinder drum facing each other are subjected to increased loading. This includes the normally present notches to avoid rapid pressure fluctuations at the control openings of the control plate. In particular, the surfaces facing each other are also stressed by rebounding of the cylinder drum or the pressure plate on to the control plate.
  • a disadvantage of the aforementioned axial piston machine is that in the presence of oil-containing flow media, the plastic layer may react to the flow medium in a disadvantageous manner, which subjects the plastic layer to increased wear.
  • vapor bubbles can form, and subsequent pressure pulses, so-called cavitation, may occur in the hydraulic medium, as well as the already mentioned rebounding of the cylinder drum or the pressure plate; the plastic layer has only insufficient resistance to such stresses and thus wears quickly, the plastic layer detaching only regionally, which results in uneven loading and faster wear.
  • An axial piston machine may provide the advantage of higher wear resistance, in particular with respect to knocking loading of the parts sliding along each other, with respect to cavitation and to the two-axle loading. Furthermore, the axial piston machine according to the example embodiment of the present invention is easier to produce and, in addition to water, may also be operated using oil-containing flow media.
  • the respective other sliding side not coated by the layer is made of steel which is hardened by nitration. This allows an easier manufacture of the sliding side lying opposite the carbon layer.
  • the use of environmentally damaging nonferrous metals may be dispensed with.
  • the layer is applied on the first sliding side or on the sliding side of the control plate. Since the control plate of an axial piston machine has smaller dimensions than the cylinder drum, the layer is able to be applied on the control plate in a simpler and more cost-effective manner.
  • control plate and/or the cylinder drum are/is generally made of metal in the region of their respective sliding sides, and if the layer is applied directly onto the metal surface of the sliding sides. The layer then adheres to the respective sliding side in a more durable manner.
  • the functional layer may be applied either directly or preferably with the aid of an adhesive layer.
  • the layer is a diamond-like, amorphous carbon layer, in particular a tetrahedral, hydrogen-free amorphous carbon layer, ta-C.
  • the ta-C layer has especially advantageous characteristics when used in an axial piston machine. For instance, the fatigue resistance of the friction- and wear-reducing layer with respect to adhesive chipping and cohesive erosion, in particular, is increased considerably, especially with respect to the stresses by cavitation and the impact forces that occur at increased operating pressure and in rapid, heavy load changes, in particular. The wear resistance is improved, especially given increased loading and contaminated flow media.
  • FIG. 1 shows a schematic representation of an axial piston machine according to an example embodiment of the present invention.
  • FIG. 2 shows cut-away portion II shown in FIG. 1 , in enlarged form.
  • FIG. 3 shows a preferred specific embodiment of a control plate of the axial piston machine according to the present invention, in a plan view of the sliding slide of the control plate.
  • FIG. 4 shows a preferred specific embodiment of a cylinder drum of the axial piston machine according to the present invention, in a plan view of the sliding side of the cylinder drum.
  • the axial piston machine illustrated in FIG. 1 is configured as swash plate with an adjustable displacement volume and one flow direction; in the conventional manner it includes a hollow-cylindrical housing 1 having an end that is open at the end face (upper end in FIG. 1 ); a connection plate 2 , which is secured to housing 1 and seals its open end; a cam plate or swash plate 3 ; a control plate 4 , which is also known as control body or control mirror; a drive shaft 5 and a cylinder drum 6 .
  • Swash plate 3 is designed as so-called tilting cradle having a semi-cylindrical cross section and, via two bearing surfaces that extend with mutual clearance parallel to the tilting direction, is supported with hydrostatic destressing at two correspondingly formed bearing shells 8 , which are mounted on the inner surface of housing end face 9 situated opposite connection plate 2 .
  • the hydrostatic destressing is implemented in a conventional manner via pressure pockets 10 formed in bearing shells 8 and supplied with pressure medium via connections 11 .
  • An actuating device 13 which is accommodated in a bulge of a cylindrical housing wall 12 , engages with swash plate 3 via an arm 14 that extends in the direction of connection plate 2 and is utilized to tilt the same about a tilting axis that is perpendicular to the tilting direction.
  • Control plate 4 is centered on the outer ring of bearing 18 and, positioned in the circumferential direction, rests against the inner surface, facing the housing interior, of connection plate 2 .
  • Control plate 4 is provided with two straight-through openings 15 in the form of kidney-shaped control slots, which are connected to, respectively, a pressure and suction line (not shown) via a pressure channel 16 D or suction channel 16 in connection plate 2 .
  • Pressure channel 16 D has a smaller flow cross section than suction channel 16 S.
  • the control surface of control plate 4 facing the housing interior and having a spherical design is used as bearing surface for cylinder drum 6 .
  • Drive shaft 5 projects into housing 1 through a through-hole in housing end face 9 and is rotatably supported in connection plate 2 with the aid of a bearing 17 in this through-hole, and with the aid of another bearing 18 it is supported in a more narrow bore section of a blind hole bore 19 widened at the end face. Furthermore, in the interior of housing 1 , drive shaft 2 penetrates centrical through-hole bore 20 in control plate 4 , a centrical through-hole bore 21 in swash plate 3 , as well as a centrical through-hole bore in cylinder drum 6 having two bore sections.
  • One of these bore sections is formed in a sleeve-shaped extension 23 , which is premolded on cylinder drum 6 , projects beyond its end face 22 facing swash plate 3 and is utilized to connect cylinder drum 6 to drive shaft 5 in a torsionally fixed manner, with the aid of a wedge-groove connection 25 .
  • the remaining bore section has a conical design. It tapers from its cross section having the largest diameter, close to the first bore section, to its cross section having the smallest diameter, close to the end or bearing surface of cylinder drum 6 resting against control plate 4 .
  • the annular space defined by drive shaft 5 and this conical bore section is denoted by reference numeral 25 .
  • Cylinder drum 6 has stepped cylinder bores 26 , which generally extend in the axial direction and are evenly disposed on a graduated circle that is coaxial with respect to the axis of the drive shaft. Cylinder bores 26 discharge directly at cylinder drum end face 22 and, via end channels 27 , at the cylinder drum bearing surface facing control plate 4 , on the same graduated circle as the control slots. One cylinder sleeve 28 in each case is inserted in the cylinder bore sections having a larger diameter and discharging directly at cylinder drum end face 22 . Cylinder bores 26 including cylinder sleeves 28 are denoted as cylinders here.
  • each slide shoe 31 On its sliding surface facing sliding pad 32 , each slide shoe 31 is provided with its own pressure pocket (not shown), which is connected to a stepped axial through channel 34 in piston 29 via a through hole 33 in slide shoe 31 and is thereby connected to the working chamber of the cylinder delimited from piston 29 in cylinder bore 26 .
  • a throttle is formed in each axial through channel 34 in the region of the assigned spherical head 30 .
  • a holding-down clamp 36 which is situated on drive shaft 5 so as to be axially displaceable, utilizing a wedge-groove connection 24 , and which is acted upon in the direction of swash plate 3 by a spring 35 , retains slide shoe 31 in contact with sliding pad 32 .
  • Axial piston machine 1 is intended for an operation using oil as flow medium.
  • Cylinder drum 6 together with pistons 29 is made to rotate via drive shaft 5 .
  • actuating device 13 When an activation of actuating device 13 has brought swash plate 3 into a tilted position relative to cylinder drum 6 , all pistons 29 execute translational movements.
  • cylinder drum 6 is rotated about 360°, each piston 29 executes an aspiration and a compression stroke during which corresponding oil flows are generated whose conveyance and evacuation is implemented via end channels 27 , control slots 15 and pressure and suction channel 16 D, 16 S, respectively.
  • each piston 29 pressurized oil flows from the individual cylinder into its pressure pocket via axial through channel 34 and through hole 33 in associated slide shoe 31 and generates a pressure field between sliding pad 32 and respective slide shoe 31 , which is utilized as hydrostatic bearing for the latter. Furthermore, via connections 11 , pressurized oil is conveyed to pressure pockets 10 in bearing shells 8 to support swash plate 3 hydrostatically.
  • Sliding surfaces 44 , 45 are formed on the facing sides of control plate 4 and cylinder drum 6 .
  • Control plate 4 has first sliding side 44
  • cylinder drum 6 has second sliding side 45 .
  • a friction- and wear-reducing layer 46 which is shown in greater detail in FIG. 2 , has been applied on first sliding side 44 , between the two sliding sides 44 , 45 .
  • Layer 46 which reduces friction and protects against wear, is evenly applied on first sliding side 44 by a PVD method (physical vapor deposition), for instance, or by the specialized arc-PVD method or a CVD method (chemical vapor deposition), preferably, however, with the aid of a PECVD method (plasma enhanced chemical vapor deposition). Furthermore, layer 46 is formed as so-called thin layer, at a thickness of up to approximately 15 micrometers, a range of 1 to 3 micrometer being endeavored.
  • a metallic adhesion layer is normally used, in particular made of Cr, Ti, Zr.
  • Second sliding side 45 of cylinder drum 6 which lies opposite layer 46 and is likewise made completely of steel, is hardened, preferably by nitration.
  • the rotational movement causes a hydrodynamic sliding film to form between layer 46 and second sliding side 45 , which is made up of the flow medium.
  • layer 46 rubs against second sliding layer 45 .
  • second sliding side 45 may briefly and rapidly drop back onto layer 46 again. This causes knocking loading, whose intensity is a function of the working pressures and the pressure fluctuation profile, in particular.
  • FIG. 3 shows a preferred specific embodiment of a control plate 4 of axial piston machine 1 according to the present invention, in a plan view of sliding side 44 of control plate 4 .
  • a kidney-shaped openings 15 which are used to control the filling and evacuation of cylinder bores 26 .
  • both openings 15 have a notch 47 at each of their ends disposed in the direction of rotation. Notches 47 cause a soft reversing and are known as such from the related art.
  • Sliding side 44 of control plate 4 is completely coated by layer 46 , the surfaces of notches 47 and the regions of the inner sides of openings 15 being included within the meaning of the present invention.
  • notches may be disposed on the end situated counter to the direction of rotation, or bores may be introduced into control plate 4 ; the surfaces of these notches (not shown) and the inner surfaces of the bores (not shown) would likewise be coated by layer 46 according to the present invention.
  • FIG. 4 shows a preferred specific embodiment of a cylinder drum 6 of axial piston machine 1 according to the present invention, in a plan view of sliding side 45 of cylinder drum 6 , which is denoted as second sliding side 45 .
  • Regions 48 which are outlined by circular rings in this figure and mark the regions at risk by cavitation, lie approximately between end channels 27 formed as elongated holes, the ends of end channels 27 being outlined as well.
  • second sliding side 45 instead of first sliding side 44 may be coated by layer 46 , the inner surfaces of end channels 27 preferably also being coated by layer 46 in this case.
  • the present invention is not restricted to the exemplary embodiments and specific embodiments.
  • the features of the exemplary embodiment and the specific embodiments may be combined with each other as desired.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
US11/632,094 2004-07-09 2005-06-08 Axial-piston machine having an antiwear layer Abandoned US20100000401A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004033321.1 2004-07-09
DE102004033321A DE102004033321B4 (de) 2004-07-09 2004-07-09 Axialkolbenmaschine mit Verschleißschutzschicht
PCT/EP2005/006156 WO2006005399A1 (de) 2004-07-09 2005-06-08 Axialkolbenmaschine mit verschleissschutzschicht

Publications (1)

Publication Number Publication Date
US20100000401A1 true US20100000401A1 (en) 2010-01-07

Family

ID=34972701

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/632,094 Abandoned US20100000401A1 (en) 2004-07-09 2005-06-08 Axial-piston machine having an antiwear layer

Country Status (5)

Country Link
US (1) US20100000401A1 (de)
EP (1) EP1769157A1 (de)
CN (1) CN101002019A (de)
DE (1) DE102004033321B4 (de)
WO (1) WO2006005399A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140150640A1 (en) * 2012-06-06 2014-06-05 Linde Hydraulics Gmbh & Co. Kg Hydrostatic Positive Displacement Machine
WO2014129926A1 (ru) * 2013-02-21 2014-08-28 Fomin Vladimir Fjodorovich Аксиально-плунжерный насос с рекуперацией энергии
US20140360351A1 (en) * 2012-08-13 2014-12-11 Kayaba Industry Co., Ltd. Fluid pressure rotary machine

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006039719A1 (de) 2006-08-24 2008-02-28 Sms Demag Ag Breitseitenplatte einer Kokille
DE102008060067B4 (de) 2008-12-02 2017-11-02 Robert Bosch Gmbh Axialkolbenmaschine mit einer Steuerplatte, die in einem Teilbereich des äußeren Dichtstegs eine erhöhte Elastizität aufweist
DE102008060491A1 (de) 2008-12-04 2010-06-10 Robert Bosch Gmbh Axialkolbenmaschine und Steuerplatte mit Verschleißschutzschicht
US9447686B2 (en) * 2010-06-23 2016-09-20 Robert Bosch Gmbh Axial piston machine having an insert ring and an insert ring for an axial piston machine
JP5425722B2 (ja) * 2010-06-23 2014-02-26 日立建機株式会社 斜軸式液圧回転機
DE102014223564A1 (de) 2014-11-19 2016-05-19 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
DE102015200310A1 (de) * 2015-01-13 2016-07-14 Robert Bosch Gmbh Kolbeneinheit und hydrostatische Radialkolbenmaschine
DE102015107343A1 (de) * 2015-05-11 2016-11-17 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Axialkolbenmaschine in Schrägachsenbauweise

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3460483A (en) * 1967-09-15 1969-08-12 Lucas Industries Ltd Port plates for hydraulic reciprocating pumps and motors
US4117770A (en) * 1976-05-13 1978-10-03 Gennady Petrovich Koshelenko Axial-piston hydraulic machine
US4799419A (en) * 1978-03-22 1989-01-24 Linde Aktiengesellschaft Multi-cylinder hydraulic piston device, a cylinder therefor, and its method of making
US5540139A (en) * 1993-01-18 1996-07-30 Danfoss A/S Hydraulic axial piston machine
US5573380A (en) * 1994-05-13 1996-11-12 Danfoss A/S Hydraulic piston machine
US5598761A (en) * 1994-11-30 1997-02-04 Danfoss A/S Hydraulic axial piston machine with control face located in rear flange and friction-reducing plastic insert in rear flange
US5622097A (en) * 1993-01-18 1997-04-22 Danfoss A/S Hydraulic piston machine
US5890412A (en) * 1994-07-13 1999-04-06 Danfoss A/S Control plate of a hydraulic machine
US6176619B1 (en) * 1996-02-20 2001-01-23 Ebara Corporation Water lubricated machine component having contacting sliding surfaces
JP2002031040A (ja) * 2000-07-12 2002-01-31 Kayaba Ind Co Ltd 液圧ピストンポンプ・モータ摺動部の表面処理構造
US20030221549A1 (en) * 2002-05-28 2003-12-04 Danfoss A/S Water-hydraulic machine
US20050025629A1 (en) * 2003-07-30 2005-02-03 Ford Michael Brent Method for protecting pump components
US6880449B1 (en) * 2001-03-30 2005-04-19 Hydro-Gear Limited Partnership Center section and running components for hydrostatic unit and method of manufacture
US6969198B2 (en) * 2002-11-06 2005-11-29 Nissan Motor Co., Ltd. Low-friction sliding mechanism
US7367783B2 (en) * 2003-03-07 2008-05-06 Honda Motor Co., Ltd. Rotating fluid machine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1963769B2 (de) * 1969-12-19 1972-01-27 Fa Constantin Rauch, 7900 Ulm Zylindertrommel Steuerplattenkombina tion fur Axialkolbenmaschinen
RU2114210C1 (ru) * 1997-05-30 1998-06-27 Валерий Павлович Гончаренко Способ формирования углеродного алмазоподобного покрытия в вакууме
DE19858483A1 (de) * 1998-12-18 2000-08-31 Mannesmann Rexroth Ag Hydraulische Verdrängermaschine, insbesondere Verdrängerpumpe
US20050002805A1 (en) * 2001-08-13 2005-01-06 Fuksa Richard C Wobble piston pump with carbon graphite cylinder
JP3999568B2 (ja) * 2002-05-24 2007-10-31 三菱重工業株式会社 表面処理ピストンを備えた流体機械

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3460483A (en) * 1967-09-15 1969-08-12 Lucas Industries Ltd Port plates for hydraulic reciprocating pumps and motors
US4117770A (en) * 1976-05-13 1978-10-03 Gennady Petrovich Koshelenko Axial-piston hydraulic machine
US4799419A (en) * 1978-03-22 1989-01-24 Linde Aktiengesellschaft Multi-cylinder hydraulic piston device, a cylinder therefor, and its method of making
US5622097A (en) * 1993-01-18 1997-04-22 Danfoss A/S Hydraulic piston machine
US5540139A (en) * 1993-01-18 1996-07-30 Danfoss A/S Hydraulic axial piston machine
US5573380A (en) * 1994-05-13 1996-11-12 Danfoss A/S Hydraulic piston machine
US5890412A (en) * 1994-07-13 1999-04-06 Danfoss A/S Control plate of a hydraulic machine
US5598761A (en) * 1994-11-30 1997-02-04 Danfoss A/S Hydraulic axial piston machine with control face located in rear flange and friction-reducing plastic insert in rear flange
US6176619B1 (en) * 1996-02-20 2001-01-23 Ebara Corporation Water lubricated machine component having contacting sliding surfaces
JP2002031040A (ja) * 2000-07-12 2002-01-31 Kayaba Ind Co Ltd 液圧ピストンポンプ・モータ摺動部の表面処理構造
US6880449B1 (en) * 2001-03-30 2005-04-19 Hydro-Gear Limited Partnership Center section and running components for hydrostatic unit and method of manufacture
US20030221549A1 (en) * 2002-05-28 2003-12-04 Danfoss A/S Water-hydraulic machine
US6969198B2 (en) * 2002-11-06 2005-11-29 Nissan Motor Co., Ltd. Low-friction sliding mechanism
US7367783B2 (en) * 2003-03-07 2008-05-06 Honda Motor Co., Ltd. Rotating fluid machine
US20050025629A1 (en) * 2003-07-30 2005-02-03 Ford Michael Brent Method for protecting pump components

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
JP2002031040-Machine translation Japanese to English *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140150640A1 (en) * 2012-06-06 2014-06-05 Linde Hydraulics Gmbh & Co. Kg Hydrostatic Positive Displacement Machine
US10024158B2 (en) * 2012-06-06 2018-07-17 Linde Hydraulics Gmbh & Co. Kg Hydrostatic positive displacement machine
US20140360351A1 (en) * 2012-08-13 2014-12-11 Kayaba Industry Co., Ltd. Fluid pressure rotary machine
US9644480B2 (en) * 2012-08-13 2017-05-09 Kyb Corporation Fluid pressure rotary machine
WO2014129926A1 (ru) * 2013-02-21 2014-08-28 Fomin Vladimir Fjodorovich Аксиально-плунжерный насос с рекуперацией энергии

Also Published As

Publication number Publication date
DE102004033321A1 (de) 2006-02-02
CN101002019A (zh) 2007-07-18
DE102004033321B4 (de) 2006-03-30
EP1769157A1 (de) 2007-04-04
WO2006005399A1 (de) 2006-01-19

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Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BECK, THOMAS;SCHATTKE, ALEXANDER;HENKE, SASCHA;AND OTHERS;REEL/FRAME:022099/0502;SIGNING DATES FROM 20061213 TO 20070126

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION