EP1789678A1 - Soupape a mouvement orbital destinee a une pompe alternative - Google Patents

Soupape a mouvement orbital destinee a une pompe alternative

Info

Publication number
EP1789678A1
EP1789678A1 EP05796351A EP05796351A EP1789678A1 EP 1789678 A1 EP1789678 A1 EP 1789678A1 EP 05796351 A EP05796351 A EP 05796351A EP 05796351 A EP05796351 A EP 05796351A EP 1789678 A1 EP1789678 A1 EP 1789678A1
Authority
EP
European Patent Office
Prior art keywords
valve
cylinder
orbit
port
intake
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Withdrawn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
EP05796351A
Other languages
German (de)
English (en)
Inventor
Harry Thomas Industries Inc. LYNN
Roy Thomas Industries Inc. ROZEK
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.)
Thomas Industries Inc
Original Assignee
Thomas Industries 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 Thomas Industries Inc filed Critical Thomas Industries Inc
Publication of EP1789678A1 publication Critical patent/EP1789678A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • 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
    • 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
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate
    • 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
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/101—Control of working-fluid admission or discharge peculiar thereto for machines with stationary cylinders
    • 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
    • F04B27/1009—Distribution members
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members

Definitions

  • the present invention comprises valves for the porting of intake and exhaust in reciprocating pumps, including vacuum pumps and compressors, and more particularly in multi-cylinder pumps such as swashplate or nutating or wobble-piston type pumps or pumps with axial pistons arranged about a central axis.
  • Passive valves such as flapper, poppet or umbrella valves
  • a flapper valve is typically made of a thin, flat material.
  • Stainless steel has been used for higher pressure flapper valve applications and elastomers have been used for small, low-pressure flapper valve applications.
  • Poppet valves are typically made of a harder material that is biased against a valve plate using a spring.
  • An umbrella valve is usually made of an elastomeric material and includes a built-in attachment method for retaining itself against the valve plate while covering several small holes. Each of these passive valve systems are activated by fluid pressure acting against the valve such that fluid is allowed to pass in one direction only.
  • Direct-acting valve systems are known. Cardillo, US 5,058,485, discloses a direct-acting orbiting ring valve for a hydraulic swashplate type pump. White, US 4,877,383, discloses a direct-acting valve such as an orbiting valve for a gerotor device. US patent 6,224,349 discloses a direct-acting orbiting valve for a swashplate type pump SUMMARY
  • the present invention provides a direct-acting, orbiting valve system for reciprocating piston pumps, including compressors and vacuum pumps, that provides greater pumping efficiency at higher speed ranges than currently feasible with passive valving systems.
  • the invention provides both intake and exhaust valve functions using a single orbiting valve member to alternately route the cylinder ports to separate intake and exhaust ports.
  • a single orbiting valve member can be provided with port routing for separate pressure and vacuum cylinders connected to the same valve plate of a multi-cylinder machine.
  • the invention reduces the ultimate torque required and the frictional losses associated with an orbiting valve member by allowing the member to rotate slightly under conditions of stiction creating a twisting motion that results in a mechanical advantage to more easily break away the stiction-adhered surfaces of the orbiting valve and the valve plate as compared to a rotary valve.
  • routing of intake and exhaust is accomplished by using concentric grooves in the orbiting valve to interconnect cylinder ports in the valve plate with the intake and exhaust ports in the valve plate.
  • the invention provides routing of intake and exhaust with discrete, non- concentric groove segments in the orbiting valve member. In this case the orbiting valve is constrained from rotating by a compliant member.
  • Figure 1 is a perspective view of a reciprocating pump which embodies the features of one embodiment of the present invention
  • Figure 2 is a side view of the pump shown in Figure 1;
  • Figure 3 is a top view of the reciprocating pump shown in Figure 1 ;
  • Figure 4 is a bottom view of the reciprocating pump shown in Figure 1 ;
  • Figure 5a is a sectional view taken along section line 5-5 of Figure 2;
  • Figure 5b is a perspective of the cross section shown in Figure 5a;
  • Figure 6a is a perspective view of the orbiting valve of the pump of Figure 1, looking into a face surface of the valve having two concentric grooves therein;
  • Figure 6b is a plan view of the orbiting valve's grooved surface shown in Figure 6;
  • Figure 7 is a perspective view of the valve plate of the pump of Figure 1, looking into a face surface of the valve plate having three cylinders emanating therefrom; for convenience of illustration the plate has been shown with a squarish shape as opposed to its actual round shape as indicated in Figures 5a, 5b;
  • Figure 8 is a perspective view of the valve plate shown in Figure 7, looking into a face surface opposite the surface shown in Figure 7;
  • Figure 9 is a face plan view of an assembly of components from the pump of Figure 1, wherein the assembly has a valve plate having three cylinders, an orbiting valve, and an eccentric interfacing the valve plate with the orbit valve; for convenience, the orbit valve circumferential projection seen in Figure 5a is not shown; also for convenience of illustration the valve plate has been shown with a squarish shape as opposed to its actual round shape as indicated in Figures 5a, 5b; wherein the view looks towards the pump's motor end, away from the pump end opposite the motor, and into the face surface of the valve plate having the cylinders emanating therefrom;
  • Figures 1 Oa-I Oe are plan views generally the same as shown in Figure 9, except for further convenience, only one cylinder and its associated cylinder port are shown; the Figures show the orbiting valve's sequence relative to stated positions of the piston;
  • Figure 11 is a partial cross sectional view taken along a longitudinal axis of a pump having an alternative embodiment of the invention , wherein the pump has its orbit valve eccentric on the opposite side of the valve plate as compared to the placement of the orbit valve in Figure 5 a;
  • Figure 12a is a face plan view of an assembly of components from a pump of the type shown in Figure 1 ; the view shows an alternative embodiment of the invention, wherein the assembly has a multi cylinder valve plate, for convenience, only one cylinder is shown; an orbiting valve having multiple segmented intake through ports and multiple segmented exhaust grooves, again for convenience, only one exhaust segment is shown; and an eccentric interfacing the valve plate with the orbiting valve, wherein the view looks towards the pump's motor end, away from the pump end opposite the motor, and into the face surface of the valve plate having the cylinders emanating therefrom;
  • Fig 12b is a perspective view of the assembly shown in Figure 12a; for convenience, the arms shown emanating from the orbiting valve in this perspective view were omitted from the plan view in Figure 12a;
  • Figures. 13 is a top perspective view of the orbiting valve eccentric of the pump of Figure 1;
  • Figure 14 is an end perspective view of the shaft, orbiting valve eccentric and orbiting valve of Figure 1 assembled together.
  • nutating or wobble-piston type compressor or pump 100 has a housing 102.
  • the housing 102 encloses a crank case volume 104.
  • the pump has certain main drive components in the housing.
  • the main drive components in the housing include shaft 18, eccentric 64, eccentric bearing 62, wobble member 60, and cross- type universal joint 56.
  • Universal joint 56 has two of its opposed arms journalled or coupled to connector 59 and the other two of its opposed arms journalled or coupled to wobble or yoke member 60.
  • the wobble member 60 has three arms 74 all of which are the same as each other. Only one arm 74 is shown. Each arm has, at its end, a ball head 76.
  • Pump 100 has three pistons, all of which are the same. Only one piston 14a, 14b is fully shown. Each piston has a piston head 14b and piston rod 14a. Each piston rod 14a is hollow and contains a socket halve 78. Each wobble member's ball head 76 is coupled to a piston rod 14a via the socket half 78.
  • each piston is associated with a respective cylinder 20a, 20b and 20c.
  • Each cylinder has associated with it a cylinder port 28a, 28b and 28c.
  • the cylinder ports 28a, 28b, 28c each comprise elongated cylinder groove port portions 28a", 28b", 28c" and small centrally located oval cylinder through port portions 28a', 28b', 28c'.
  • the small oval portions are the only portions of the cylinder ports that actually pass through the valve plate.
  • the center of UV joint 56 is aligned along the center the shaft axis 18a.
  • drive shaft 18 is rotated by the motor 58 , the stator of which is affixed to the end cover 52, which is affixed, via wall 103, to housing 102 to enclose orbiting valve 16, orbiting valve eccentric 30, orbiting valve eccentric bearing 32 and counter moment mass 54.
  • eccentric 64 As the motor shaft 18 rotates, eccentric 64, through bearing 62, causes wobble member 60 to wobble and thereby drive rod 14a in a predominantly reciprocating motion.
  • Orbiting valve eccentric 30, acting through orbiting valve eccentric bearing 32 causes orbiting valve 16 to orbit about the shaft centerline 18 as it slides relative to the valve plate 25.
  • Groove 22 can be described as a pressure or exhaust groove and groove 24 can be described as an intake groove.
  • the dashed line in Figures. 5a, 5b. indicates fluid communication between exhaust port 26 shown in Fig. 9 and connector tube 46 shown in Fig. 5 a. Fluid intake is routed through port 44 of the attenuation chamber 48 , through ports 42 into the crankcase chamber 104 and then through valve intake port 27.
  • the arrows in Fig. 5a, 5b show the fluid flow direction.
  • Fig. 5a and Fig. 5b show piston rod 14a in a top dead center position such that cylinder through port 28a is no longer connected to exhaust groove 22 or intake groove 24.
  • FIG. 10a- 1Oe the orbiting valve sequence can be further seen.
  • FIG. 10a for ease of reference, only one cylinder 20a and its associated cylinder port 28a are shown. Also, for ease of reference, the projection 16c is not shown.
  • Each of the other cylinders 20b, 20c are going through exactly the same sequence except the cylinders are 120° out of phase with each other.
  • the direction of orbit valve 16 is indicated by arrow 70 and is counterclockwise.
  • the angular orientation of the shaft 18 relative to orbit valve 16 during the sequence is marked by darkened area 30a. The degrees of rotation can thus be correlated to the piston's position.
  • the orbit valve 16 is not restrained from rotation about its own axis, but since the grooves 22 and 24 are circular the orbit valve can rotate as well as orbit, although the rotation about its own axis does not affect its operation.
  • the combination of bearing 32 and the friction of the orbit valve 16 against the valve plate 25 would result in the motion being largely orbital with only little, if any, rotation. Further the grooves 22 and 24 do not pass through the orbit valve to form a through space.
  • a further feature that can be included in a pump embodying the invention is an axial spring bias force 86 that may be provided between the orbiting valve 16 and a stationary structure attached to the housing, such as end cover 52.
  • the spring serves to overcome the net separation forces caused by the difference between (1) the fluid pressure acting on an area of the surface of the orbiting valve 16 contacting the valve plate 25 and (2) the fluid pressure acting on the surface of the orbit valve opposite the orbit valves sealing surface.
  • the spring assures sealing between the land areas surrounding the grooves 22, 24 and the valve plate 25 of housing 102.
  • one or more axially extending springs could provide a biasing force between the orbiting valve 16 and eccentric 30.
  • a circumferential projection 16c is provided on the valve's end wall surface opposite the valve surface having the concentric grooves.
  • the circumferential projection defines a space to receive an end coil of spring 86.
  • the projection of course does not have to be continuous.
  • a groove can be provided to receive an end coil of the spring.
  • the spring 86 is not shown in its actual relative coiled and flexed state.
  • FIG. 12a and 12b an alternative embodiment having a segmented orbit valve with a combination of grooved segments and through segments is shown.
  • the associated valve plate 225 would have 3 cylinders, for convenience only one cylinder 220a is shown.
  • the valve plate would have three cylinder ports, again for convenience only, port 228a, comprising groove portion 228a" and through portion 228a' is shown.
  • the valve plate further has three exhaust ports; for convenience only one 226a is shown.
  • the orbiting valve 216 shown in Figures 12b and 12a has three intake segments 224a, 224b, 224c; each would be uniquely associated with one of the three cylinders.
  • intake 224a is associated with cylinder 220a.
  • the intake segments completely pass through the orbit valve. Having the intake segments as through apertures, allows for direct intake into the associated cylinder port, thus eliminating the need for any intake ports in the valve plate.
  • the orbiting valve of Figures 12a and 12b would also have three grooved segmented exhaust ports; for convenience only exhaust port 222a is shown. Each exhaust port segment is uniquely associated with a cylinder and a cylinder port. In the shown embodiment grooved exhaust segment 226a is associated with cylinder port 228a and cylinder 220a. The exhaust segments do not pass through the orbit valve.
  • the orbit valve would have a projection similar to the projection 16c shown in Figures 5a,5b. For convenience, the projection is not shown in Figures 12a, 12b.
  • the embodiment in Figures 12a and 12b show their intake segment as passing through the orbit valve; they do not have to pass through the orbit valve. In this case, proper intake porting through the valve plate would have to be provided.
  • the exhaust segments as pass through holes thereby eliminating the need for exhaust ports in the valve plate.
  • the cavity in which the orbit valve is enclosed would have to be pressure sealed.
  • the pressure allowed to build up in the cavity could be made sufficient to overcome the net separation forces between the valve plate and orbit valve so as to eliminate the need for an external biasing force member such as spring 86.
  • the amount of pressure allowed to act as the biasing force should not be so great as to create undue friction forces between the orbit valve and valve plate.
  • the pressure could be regulated by a pressure regulation port in the cavity or some or some other pressure regulator.
  • the orbit valve 216 must be prevented from rotating relative to the housing by use of any of several possible methods including but not limited to an Oldham coupling, one or more idler crank mechanisms, one or more torsional springs, one or more leaf springs, or other compliant mechanisms either separately attached between the disk and the stationary housing or integrated as a monolithic member with the disk itself.
  • an Oldham coupling one or more idler crank mechanisms, one or more torsional springs, one or more leaf springs, or other compliant mechanisms either separately attached between the disk and the stationary housing or integrated as a monolithic member with the disk itself.
  • four integral flexible compliant arms 216d are shown only in the perspective view 12b.
  • a spring and projection similar to spring 86 and projection 16c could also be used to form a resilient compliant.
  • the projection used to receive an end coil of the spring would be sized so that the circumferential projection forms a cavity which permits the end coil to snap-fit into the cavity.
  • the snap-fit would serve to couple the spring to the orbit valve with a sufficient frictional fit to resist the torsion forces imparted to the orbit valve by the eccentric. If a groove were used to receive the spring, the groove could have a cavity therein to receive a spring end and thereby limit the orbit valves rotation.
  • orbit valve 216 could be used with a pump having compression and vacuum cylinders.
  • the cylinders would be a combination of compression and vacuum cylinders. Each cylinder would be associated with a combination of orbit valve intake/exhaust cavities, which could be combinations of grooves, or through ports.
  • the valve plate and orbit valve would be configured to interconnect the pressure and vacuum cylinders provided within the same pump to the appropriate intake or exhaust ports in the valve plate to sequence and to provide both vacuum and pressure pumping capability with separate fluid circuits; or to provide a combination of pumping and motoring using either a pressure or vacuum fluid source and/or an electric motor in any combination.
  • the eccentric 30 could include a portion (not shown) that acts as a counter weight to dynamically balance the primary radial dynamic forces created by the orbiting motion of the orbit valve 16.
  • counter moment mass 54 would contain a counter moment mass to dynamically balance both the primary drive mechanism unbalance moment of the pump or motor and the unbalance moment created by the orbit valve and its eccentric counter mass being located in two different axial planes.
  • the orbit valve eccentric 330 may be on the same side of valve plate 325 as the eccentric 64. See Fig. 11. In this case, the eccentric 330 is coupled directly to eccentric 64. Eccentric 64 imparts an orbiting motion to eccentric 330 by way of eccentric bearings 332. Eccentric 330 imports an orbiting motion to orbit valve 316 with coupling 300.
  • orbit valve cavities 22, 24 have been described as grooves 22, 24, they can also be passages, channels or ducts. Additionally, although both 22 and 24 are described as grooves, they could comprise a combination of grooves and pass through apertures. In this case the porting of the valve plate would follow the principles described with regards to Figures 12a, 12b.
  • the orbit valve can have a variety of shapes beyond those shown or described.
  • the valve plate and housing can also have a variety of shapes beyond those disclosed.
  • coupling is used inclusively herein to cover both direct and indirect coupling.
  • the shaft 18 is coupled to the wobble member 60 by way of an indirect coupling.
  • the shaft is also coupled to the piston 14a, 14b by way of an indirect coupling.

Landscapes

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

Abstract

L'invention concerne une soupape à mouvement orbital destinée à des pompes, des compresseurs, et des moteurs pneumatiques ou hydrauliques équipés de cylindres multiples tels que des pompes du type à plateau ou à disque oscillant et des compresseurs à pistons axiaux agencés autour d'un axe central, ladite soupape étant connectée par l'intermédiaire d'un excentrique et d'un palier à un arbre et amenée à décrire une orbite autour d'un axe de l'arbre par rotation de cet arbre. Des rainures ménagées dans la surface de la soupape à mouvement orbital connectent alternativement un orifice de chaque cylindre avec une admission fixe et un orifice d'échappement de la plaque de soupape temporisé afin d'obtenir une performance optimale indépendamment du différentiel de pression, autrement nécessaire pour ouvrir ou fermer un clapet passif ou des appareils de réglage de pression à clapet. Le déplacement orbital permet à une soupape d'agir directement sur des fonctions d'admission et d'échappement avec un déplacement relativement plus petit et une friction de loin inférieure à celle d'une soupape rotative de dimension semblable.
EP05796351A 2004-09-15 2005-09-15 Soupape a mouvement orbital destinee a une pompe alternative Withdrawn EP1789678A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US61001304P 2004-09-15 2004-09-15
PCT/US2005/032856 WO2006031935A1 (fr) 2004-09-15 2005-09-15 Soupape a mouvement orbital destinee a une pompe alternative

Publications (1)

Publication Number Publication Date
EP1789678A1 true EP1789678A1 (fr) 2007-05-30

Family

ID=36060376

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05796351A Withdrawn EP1789678A1 (fr) 2004-09-15 2005-09-15 Soupape a mouvement orbital destinee a une pompe alternative

Country Status (8)

Country Link
US (1) US20080075616A1 (fr)
EP (1) EP1789678A1 (fr)
JP (1) JP2008513649A (fr)
CN (1) CN101018949A (fr)
AU (1) AU2005284802A1 (fr)
CA (1) CA2580022A1 (fr)
GB (1) GB2432197A (fr)
WO (1) WO2006031935A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2783150B1 (fr) * 2011-11-22 2020-05-13 Graco Minnesota Inc. Pompe de graissage de boîtes
CN105332871B (zh) * 2015-11-20 2017-07-25 西安交通大学 分散式杯状缸体与滚动轴承支撑的斜盘式轴向柱塞泵
US11408407B2 (en) 2016-07-25 2022-08-09 Caire Inc. Wobble plate compressor and oxygen concentrator using the same
CN113166693A (zh) * 2019-01-11 2021-07-23 日商乐华生命科學有限公司 能够对应气体灭菌的驱动机构

Family Cites Families (10)

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Publication number Priority date Publication date Assignee Title
US2732808A (en) * 1956-01-31 Fluid pump and control
US1774663A (en) * 1929-07-24 1930-09-02 Arthur S Parks Pump
US2142086A (en) * 1933-09-09 1939-01-03 Ex Cell O Corp Fuel pump
US2579879A (en) * 1949-12-10 1951-12-25 Sundstrand Machine Tool Co Gyratory valve for hydraulic pumps or motors
US5058485A (en) * 1986-11-04 1991-10-22 Cardillo Joseph S Ring valve pump
US4877383A (en) * 1987-08-03 1989-10-31 White Hollis Newcomb Jun Device having a sealed control opening and an orbiting valve
US5733105A (en) * 1995-03-20 1998-03-31 Micropump, Inc. Axial cam driven valve arrangement for an axial cam driven parallel piston pump system
JP2000073946A (ja) * 1998-08-27 2000-03-07 Denso Corp 圧縮機
US6572344B1 (en) * 2001-11-26 2003-06-03 Caterpillar Inc Compact pump or motor with internal swash plate
US6651794B2 (en) * 2001-12-07 2003-11-25 Caterpillar Inc Hydro-mechanical combiner

Non-Patent Citations (1)

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Title
See references of WO2006031935A1 *

Also Published As

Publication number Publication date
CA2580022A1 (fr) 2006-03-23
JP2008513649A (ja) 2008-05-01
WO2006031935A1 (fr) 2006-03-23
CN101018949A (zh) 2007-08-15
GB2432197A (en) 2007-05-16
AU2005284802A1 (en) 2006-03-23
WO2006031935B1 (fr) 2006-05-11
GB0704521D0 (en) 2007-04-18
US20080075616A1 (en) 2008-03-27

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