EP1748187A2 - Plaque de soupapes résistant à l'usure pour un dispositif de transfert de fluide - Google Patents

Plaque de soupapes résistant à l'usure pour un dispositif de transfert de fluide Download PDF

Info

Publication number
EP1748187A2
EP1748187A2 EP06117743A EP06117743A EP1748187A2 EP 1748187 A2 EP1748187 A2 EP 1748187A2 EP 06117743 A EP06117743 A EP 06117743A EP 06117743 A EP06117743 A EP 06117743A EP 1748187 A2 EP1748187 A2 EP 1748187A2
Authority
EP
European Patent Office
Prior art keywords
port plate
rotor
housing
body portion
wear layer
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Withdrawn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
EP06117743A
Other languages
German (de)
English (en)
Other versions
EP1748187A3 (fr
Inventor
Steven E. Sund
James V. Guiheen
Jr Richard G. Rateick
Charles J Gasdaska
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.)
Honeywell International Inc
Original Assignee
Honeywell International Inc
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 Honeywell International Inc filed Critical Honeywell International Inc
Publication of EP1748187A2 publication Critical patent/EP1748187A2/fr
Publication of EP1748187A3 publication Critical patent/EP1748187A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F04B1/2042—Valves
    • 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
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0403—Refractory metals, e.g. V, W
    • F05C2201/0409—Molybdenum
    • 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
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0418—Noble metals
    • F05C2201/0421—Silver
    • 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
    • F05C2201/00—Metals
    • F05C2201/04—Heavy metals
    • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0466—Nickel
    • 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
    • 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
    • F05C2203/0813—Carbides
    • F05C2203/0817—Carbides of silicon
    • 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
    • F05C2203/0813—Carbides
    • F05C2203/0826—Carbides of wolfram, e.g. tungsten carbide

Definitions

  • the present invention is directed to a port plate having a wear layer formed from a wear resistant material and a body portion formed from a second material and to a fluid transfer device including such a port plate, and, more specifically, toward a port plate having a ceramic or cermet wear layer connected to a metallic body portion and to a fluid transfer device including such a port plate.
  • Fluid transfer devices are known that can be operated in a first direction as a pump and in a second direction as a motor. These devices may comprise a housing within which a rotor rotates with respect to a port plate and a cam plate angled with respect to the rotor's axis of rotation.
  • the rotor includes a bore or bores for receiving one or more (generally an odd number) of pistons. One end of each piston is held against to the cam plate. As the rotor rotates with respect to the housing, each piston moves axially with respect to the rotor and the port plate.
  • the port plate includes a fluid inlet through which a fluid enters the housing when a piston aligned with the fluid inlet moves away from the port plate and a fluid outlet through which fluid exits the housing when a piston aligned with the fluid outlet moves toward the port plate.
  • the fluid transfer device When the rotor is connected to a source of power, it causes the-pistons to draw fluid from the inlet and expel fluid through the outlet; when operated in this manner, the fluid transfer device is referred to as an axial piston pump.
  • the fluid transfer device When fluid is applied under pressure to the fluid inlet and drawn from the fluid outlet at a lower pressure, the rotor is caused to turn by the pressure difference, and the fluid transfer device is referred to as a hydraulic motor.
  • axial piston pump and “hydraulic motor” may refer to the same fluid transfer device, depending on the what is causing the rotation of the rotor.
  • the position of either the rotor or the port plate should generally be adjustable to control the clearance therebetween. If the position of the rotor is adjustable, the fluid transfer device is referred to as a "floating rotor" fluid transfer device. However, it may be difficult to dynamically control the position of a rotor in such a device. In floating rotor devices a constant force is generally applied against a port plate under all operating conditions. This can lead to excessive drag between the rotor and port plate at low pressures and to excessive leakage at higher pressures.
  • the device When the position of the port plate is variable, the device is referred to as a "floating port plate" fluid transfer device.
  • Such devices generally include one or more balance pistons for dynamically adjusting the position of the port plate as the device operates.
  • Such floating port plates can thus be adjusted to minimize drag at low pressures and control leakage at higher pressures.
  • these port plates with their various openings for accommodating balance pistons and flow channels for carrying fluids to and from the port plate, are more complex than the port plates used with floating rotor devices.
  • a fluid transfer device that includes a housing having an interior, a cam surface in the interior and a port plate in the interior opposite the cam surface-
  • the port plate includes a body portion formed from a first material and a wear layer formed from a second material.
  • the fluid transfer device further includes a rotor mounted in the housing for rotation relative to the housing and the port plate.
  • the rotor includes at least one axial opening and has a surface contacting the port plate wear layer.
  • At least one piston is mounted in the at least one opening that has a first end contacting the cam surface, the piston reciprocating in the at least one opening as the rotor rotates relative to the port plate.
  • Another aspect of the invention comprises a fluid transfer device that includes a housing having an interior, a cam surface in the interior and a port plate in the interior opposite the cam surface.
  • the port plate has a body portion formed from a first material and a wear layer formed of a second material.
  • a rotor is mounted in the housing for rotation relative to the housing and the port plate and includes at least one axial opening and a surface contacting the port plate wear layer.
  • Pistons are mounted in the axial openings and each has a first end contacting the cam surface so that the piston reciprocates in the opening as the rotor rotates relative to the port plate.
  • An additional aspect of the invention comprises a fluid transfer device that includes a housing having an interior and a cam plate in the interior.
  • a floating port plate is mounted in the interior opposite the cam surface and includes a body portion formed from a first material and having a fluid inlet and a fluid outlet and a wear layer formed of a second material and having a first through-opening aligned with the fluid inlet and a second through-opening aligned with the fluid outlet.
  • a brazed interlayer which may include a silver alloy, connects the wear layer to the body portion.
  • a rotor is mounted in the housing for rotation relative to the housing and the port plate and includes at least one axial opening and a surface contacting the port plate wear surface. Pistons are mounted in the openings, each having a first end contacting the cam surface, the pistons reciprocating in the openings as the rotor rotates relative to the cam surface.
  • a biasing device biases the port plate against the rotor.
  • FIG. 1 illustrates a fluid transfer device 10 according to an embodiment of the present invention comprising a housing 12 having an interior 14 in which a rotor 16 is mounted for rotation.
  • Rotor 16 is supported by first and second sets of bearings 18 and comprises a rotor shaft 20 and a rotor body 22.
  • Rotor body 22 includes a plurality of cylinders 24, two of which are illustrated in Figure 1. Generally, an odd number of cylinders will be provided.
  • Rotor body 22 includes a balance land or front face 26 having first and second openings 28 communicating with cylinders 24.
  • First and second pistons 30 are mounted for sliding movement in cylinders 24 in an axial direction generally parallel to the axis 32 of rotor shaft 20.
  • Each of pistons 30 includes a first end 34 facing openings 28 and a second end 36 projecting from rotor body 22 and terminating in a shoe assembly 38.
  • a cam plate 40 (also known as a swash plate) is mounted in interior 14 of housing 12, and shoe assembly 38 are slidably mounted thereagainst.
  • a port plate 42 is mounted at the end of housing 12 opposite cam plate 40.
  • Port plate 42 includes a body portion 44 formed from a metal or alloy such as, for example, titanium or a titanium alloy or steel such as a stainless steel.
  • Body portion 44 includes an inlet 46 having a first portion 48 with a first diameter and a second portion 50 having a second diameter smaller than the diameter of the first portion 48 and an outlet 45 having a first portion 47 with a first diameter and a second portion 49 having a second diameter smaller than the diameter of the first portion 47.
  • Body portion 44 further includes an opening 52 for receiving a balance piston 54 illustrated in Figure 4.
  • Port plate 42 further includes a wear layer 56 including a first arcuate inlet opening 58 communicating with inlet 46 of body portion 44 and a second arcuate outlet opening 60 communicating with outlet 45 of body portion 44.
  • Wear layer 56 is preferably formed from a ceramic or cermet and is approximately 0.1 inch thick. Suitable wear layer materials include, for example, silicon nitride, silicon carbide, aluminum oxide, tungsten-carbide cobalt, ceramic matrix composites, metal matrix composites and titanium carbide particulate-silicon carbide whisker-reinforced aluminum oxide.
  • the coefficient of thermal expansion of metal is significantly greater than that of most ceramics and cermets.
  • the operating temperature range of the fluid transfer device can range from well below 0° F to many hundreds of degrees. Thus, joints between such material can be severely stressed and may fail if not formed in an appropriate manner.
  • an interlayer 62 is provided between wear layer 56 and body portion 44.
  • This interlayer 62 helps compensate for the different thermal expansion coefficients of the two materials and to distribute stresses and strains in a manner that allows the port plate to survive the extreme variations in temperature that it encounters in normal use and during manufacturing. Stresses are controlled in interlayer 62 by allowing for creep, plasticity, and yielding of the interlayer materials.
  • the interlayer 62 provides a thermal expansion gradient between the low expansion ceramic and high expansion metal.
  • the brazed interlayer structure must also act as a seal to prevent leakage. When used in an environment where jet fuel is present, braze materials and metals must be carefully selected so as not to react with the jet fuel.
  • interlayer 62 includes a first layer of braze 70 on body portion 44, a first layer of nickel 72, a second layer of braze 74, a layer of molybdenum 76, a third layer of braze 78, a second layer of nickel 80, and fourth layer of braze 82 connecting wear layer 56 to body portion 44.
  • a suitable brazing alloy containing silver, copper and titanium (95% Ag, 5% copper and titanium) is available from Wesgo Metals of Hayward, California as part of their Active Brazing Alloy line under the trade name "Silver ABA.” It is believed that gold- and palladium-containing alloys would also be suitable, but these tend to be more expensive than Silver ABA.
  • the use of interlayer structures for joining ceramics and metals is discussed in U.S. Patent 6,131,797 to Gasdaska and in U.S. Patent 6,655,695 to Sund which patents are both hereby incorporated by reference in their entireties.
  • each layer will depend on the particular application. Testing and computer simulitions suggest that titanium alloy (Ti-6-4) for body portion 44, and 0.01 inch layers Silver ABA for the braze provide satisfactory results.
  • the nickel layers were also selected to be 0.01 inch thick while a molybdenum layer 0.09 inches thick was used. Nickel thicknesses ranging from 0.01 to 0.03 inches and Molybdenum thicknesses of about 0.05 to 0.09 were also contemplated and simulated. These thicknesses appear to provide adequate, but not superior, results.
  • body portion 44 of port plate 42 may include a relatively complex passageways and chambers.
  • body portion 44 is formed from a metal or metal alloy, it is relatively easy to cast, machine, or otherwise work into a suitable configuration using common metalworking techniques.
  • the metal or metal alloy also possesses great strength and is relatively unlikely to crack or rupture even when exposed to high pressures over a wide range of operating temperatures during use.
  • the ceramic or cermet of wear layer 56 includes first and second arcuate openings 58, 60. These are formed as through openings, however, and therefore can be formed relatively easily in the ceramic material (as opposed to the blind bores that would be required in a solid ceramic port plate).
  • a port plate is provided with a highly wear resistant layer that does not require complex and expensive machining and a body portion 44 that is strong and easy to machine. It is believed that, even though the addition of interlayer 62 adds to the complexity of port plate 42 as compared to a solid ceramic port plate, the reduced use of expensive ceramic material and simplified machining and greater reliability provided by the inventive design will provide an overall cost savings.
EP06117743A 2005-07-26 2006-07-24 Plaque de soupapes résistant à l'usure pour un dispositif de transfert de fluide Withdrawn EP1748187A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/188,651 US20070022873A1 (en) 2005-07-26 2005-07-26 Wear-resistant port plate for a fluid transfer device and fluid transfer device including same

Publications (2)

Publication Number Publication Date
EP1748187A2 true EP1748187A2 (fr) 2007-01-31
EP1748187A3 EP1748187A3 (fr) 2007-10-10

Family

ID=37114357

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06117743A Withdrawn EP1748187A3 (fr) 2005-07-26 2006-07-24 Plaque de soupapes résistant à l'usure pour un dispositif de transfert de fluide

Country Status (2)

Country Link
US (1) US20070022873A1 (fr)
EP (1) EP1748187A3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2835079A1 (es) * 2019-12-19 2021-06-21 Danfoss As Conjunto de placa de válvulas

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10309380B2 (en) 2011-11-16 2019-06-04 Ocean Pacific Technologies Rotary axial piston pump
US10094364B2 (en) 2015-03-24 2018-10-09 Ocean Pacific Technologies Banded ceramic valve and/or port plate
EP4151890B1 (fr) * 2021-09-16 2023-10-04 Danfoss A/S Machine hydraulique

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4934251A (en) * 1988-12-16 1990-06-19 Allied-Signal Inc. Hydraulic motor or pump with constant clamping force between rotor and port plate
US5622097A (en) * 1993-01-18 1997-04-22 Danfoss A/S Hydraulic piston machine
US6131797A (en) * 1998-11-16 2000-10-17 Alliedsignal Inc. Method for joining ceramic to metal
US6287086B1 (en) * 2000-02-23 2001-09-11 Eaton Corporation Hydraulic pump with ball joint shaft support
US6655695B1 (en) * 2001-02-13 2003-12-02 Honeywell International Inc. Face seal assembly with composite rotor
US6880449B1 (en) * 2001-03-30 2005-04-19 Hydro-Gear Limited Partnership Center section and running components for hydrostatic unit and method of manufacture

Family Cites Families (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2785913A (en) * 1954-04-20 1957-03-19 Crane Packing Co Rotary mechanical seal with ceramic seat
US3025069A (en) * 1957-01-14 1962-03-13 Bell & Gossett Co Seat for rotary mechanical seals
US3048413A (en) * 1959-10-15 1962-08-07 Douglas Aircraft Co Inc Rotating shaft seal
US3249061A (en) * 1963-07-01 1966-05-03 Sundstrand Corp Pump or motor device
US3523678A (en) * 1968-03-13 1970-08-11 Lucas Industries Ltd Valve plate for a hydraulic pump or motor
US3810637A (en) * 1972-01-14 1974-05-14 Mecanique Ind Int Shaft packing
JPS5228041A (en) * 1975-08-29 1977-03-02 Nissan Motor Co Ltd Wear-resistant sliding member
CH633868A5 (de) * 1977-09-07 1982-12-31 Alusuisse Verschleissfeste beschichtung der arbeitsoberflaeche von scheibenfoermigen maschinenteilen aus aluminium oder aluminiumlegierungen.
US4391450A (en) * 1982-08-30 1983-07-05 Electrochemical Technology Corp. Shaft seal resistant to electrokinetic corrosion
US4451048A (en) * 1982-09-28 1984-05-29 Pick Steve J High speed shaft seal
IT1174800B (it) * 1983-11-21 1987-07-01 Alberto Bartorelli Metodo per la determinazione di immunoglobuline umane specifiche per gli antigeni dei carcinomi umani e sua utilizzazione nella sierodiognosi di forme primitive tumorali
US4772294A (en) * 1985-07-05 1988-09-20 The General Electric Company Brazed composite compact implements
JPS6278172A (ja) * 1985-09-30 1987-04-10 日本特殊陶業株式会社 セラミツクと金属との接合構造
EP0265264A3 (fr) * 1986-10-23 1989-10-11 Denis Michael William Winslow Dispositif de protection d'étanchéité
CH677266A5 (fr) * 1986-10-28 1991-04-30 Pacific Wietz Gmbh & Co Kg
US4815747A (en) * 1988-02-01 1989-03-28 The Gorman-Rupp Company Face type seal assembly
US5048654A (en) * 1990-07-20 1991-09-17 Borg-Warner Automotive, Inc. Ceramic clutch separator plates
US5108025A (en) * 1991-05-20 1992-04-28 Gte Laboratories Incorporated Ceramic-metal composite article and joining method
US5234152A (en) * 1992-01-07 1993-08-10 Regents Of The University Of California Transient liquid phase ceramic bonding
US5372298A (en) * 1992-01-07 1994-12-13 The Regents Of The University Of California Transient liquid phase ceramic bonding
US5337961A (en) * 1992-12-07 1994-08-16 General Electric Company Ceramic tip and compliant attachment interface for a gas turbine fuel nozzle
US5407119A (en) * 1992-12-10 1995-04-18 American Research Corporation Of Virginia Laser brazing for ceramic-to-metal joining
US5909879A (en) * 1993-03-09 1999-06-08 Norton Company Diamond film coating for mating parts
US5626347A (en) * 1994-09-29 1997-05-06 Alliedsignal Inc. Coning resistant face seal having a "U" shape
US5544896A (en) * 1995-02-06 1996-08-13 Alliedsignal Inc. Composite face seal
JPH09144893A (ja) * 1995-11-27 1997-06-03 Hitachi Ltd メカニカルシール及び遠心圧縮機
US6113109A (en) * 1998-04-20 2000-09-05 Fel-Pro Incorporated Expanded graphite gasket with beaded stress risers
US6520703B1 (en) * 2000-09-13 2003-02-18 Honeywell International, Inc. Coupling with tribological coating system
JP3920551B2 (ja) * 2000-09-29 2007-05-30 株式会社山武 接合方法
US6450762B1 (en) * 2001-01-31 2002-09-17 General Electric Company Integral aft seal for turbine applications
US6679678B2 (en) * 2002-05-31 2004-01-20 Honeywell International, Inc. Increased wear-life mechanical face seal anti-rotation system
US6774073B2 (en) * 2002-07-29 2004-08-10 Coorstek, Inc. Graphite loaded silicon carbide and methods for making
JP4049082B2 (ja) * 2003-06-19 2008-02-20 株式会社豊田自動織機 圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4934251A (en) * 1988-12-16 1990-06-19 Allied-Signal Inc. Hydraulic motor or pump with constant clamping force between rotor and port plate
US5622097A (en) * 1993-01-18 1997-04-22 Danfoss A/S Hydraulic piston machine
US6131797A (en) * 1998-11-16 2000-10-17 Alliedsignal Inc. Method for joining ceramic to metal
US6287086B1 (en) * 2000-02-23 2001-09-11 Eaton Corporation Hydraulic pump with ball joint shaft support
US6655695B1 (en) * 2001-02-13 2003-12-02 Honeywell International Inc. Face seal assembly with composite rotor
US6880449B1 (en) * 2001-03-30 2005-04-19 Hydro-Gear Limited Partnership Center section and running components for hydrostatic unit and method of manufacture

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2835079A1 (es) * 2019-12-19 2021-06-21 Danfoss As Conjunto de placa de válvulas
US11555488B2 (en) 2019-12-19 2023-01-17 Danfoss A/S Valve plate assembly

Also Published As

Publication number Publication date
EP1748187A3 (fr) 2007-10-10
US20070022873A1 (en) 2007-02-01

Similar Documents

Publication Publication Date Title
US6918594B2 (en) Face seal assembly with composite stator
EP1748187A2 (fr) Plaque de soupapes résistant à l'usure pour un dispositif de transfert de fluide
RU2432445C2 (ru) Модульное буровое долото с неподвижными режущими элементами, корпус данного модульного бурового долота и способы их изготовления
EP2609290B1 (fr) Pièce d'usure
NZ503937A (en) Transfers pressure energy from one fluid system to another characterised using a metallic components to decrease strains in pipe couplings leading to elastic deformations
Fernandez et al. Active metal brazing of silicon nitride ceramics using a Cu-based alloy and refractory metal interlayers
US3898917A (en) Variable displacement fluid translating device
EP1540174B1 (fr) Palier de couronne a cames pour systeme d'alimentation en combustible
EP1467129B1 (fr) Segment de piston de pulverisation
US9279289B2 (en) Combination mud motor flow diverter and tiled bearing, and bearing assemblies including same
JP2022506443A (ja) ハイブリッド動圧静水圧スラスト軸受のシステム及び方法
EP1441111B1 (fr) Soupape de faible poids pour moteur à combustion interne
US10094364B2 (en) Banded ceramic valve and/or port plate
CN101337577A (zh) 多手指、多关节水下作业用水压驱动机械手
US11566718B2 (en) Valves, valve assemblies and applications thereof
JP5642297B2 (ja) ベーン型圧縮機
CN111828242A (zh) 一种锥柱塞斜轴马达和旋挖钻机
US20050241434A1 (en) Use of a transmission component of a metal matrix composite (MMC) material
JP6190804B2 (ja) ピストンポンプ・モータ
EP3715634B1 (fr) Palier de pompe à engrenages comportant un arrêt de tampon hybride
JP3852902B2 (ja) 耐摩耗性に優れた摺動部材
JPH09209920A (ja) 可変容量型斜板式液圧機械及び静油圧伝動装置
CN110873196A (zh) 阀、阀组件及其应用
JP4267891B2 (ja) シール部品
EP1845277A2 (fr) Plaquette de frein à disque pour bicyclette avec matériau de friction en fibre de titane

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

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

RIC1 Information provided on ipc code assigned before grant

Ipc: F03C 1/06 20060101ALI20070904BHEP

Ipc: F04B 1/20 20060101AFI20061027BHEP

17P Request for examination filed

Effective date: 20080307

17Q First examination report despatched

Effective date: 20080411

AKX Designation fees paid

Designated state(s): DE FR GB

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20100413