EP0853726B1 - Doppelpumpe mit ladepumpe - Google Patents
Doppelpumpe mit ladepumpe Download PDFInfo
- Publication number
- EP0853726B1 EP0853726B1 EP96928452A EP96928452A EP0853726B1 EP 0853726 B1 EP0853726 B1 EP 0853726B1 EP 96928452 A EP96928452 A EP 96928452A EP 96928452 A EP96928452 A EP 96928452A EP 0853726 B1 EP0853726 B1 EP 0853726B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump unit
- double pump
- unit according
- coupling piece
- piece
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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
- F04B1/22—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 having two or more sets of cylinders or pistons
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
- F04B23/106—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being an axial piston pump
-
- 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
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/14—Combinations of two or more pumps the pumps being of different types at least one pump being of the non-positive-displacement type
Definitions
- the invention relates to a double pump unit according to the preamble of the claim 1.
- Such a double pump unit is known from DE-OS 33 24 583.
- the known double pump unit has two hydraulic pumps with coaxial to each other arranged drive shafts, which are non-positively connected to one another by means of a coupling piece are coupled on.
- the coupling piece is designed in the form of a hollow shaft and by means of a spline / groove toothing with the free drive shaft ends of the two Hydraulic pumps connected.
- the coupling piece is from a connector enclosed that the suction and pressure channels leading to the hydraulic pumps receives.
- the double pump unit known from DE-OS 33 24 583 sucks this in conveying pressure medium directly from a low pressure line without the To subject the media to pre-compression beforehand. This is the Efficiency of the known double pump unit is limited and there is also Risk of damage due to cavitation in the intake ducts.
- DE-PS 30 18 711 To connect a hydraulic pump to a charge pump.
- the charge pump consists of one Turbine-like impeller, which is in a suitably trained chamber rotates.
- the present invention has the object based on developing a hydrostatic double pump unit so that a Charge pump is integrated in a structurally simple and inexpensive manner.
- the connector Pre-pressure chamber provided in which the intake ducts open.
- the Coupling piece has peripherally arranged blade elements which in the Pre-pressure chamber rotate and thus the pressure medium under a pre-pressure in the Feed intake ducts.
- the invention is based on the knowledge that the already existing and with the drive shaft rotating coupling piece as a paddle wheel for the Charge pump can be used if a corresponding pre-pressure chamber in the Connection piece is provided and the coupling piece with corresponding Bucket elements is provided. This solution requires only a minor one additional design effort and is therefore particularly inexpensive.
- the connector can be in two parts, consisting of one Main body and a lid-like closure part closing this, formed his.
- the coupling piece with its blade elements by a appropriately sized opening in the main body through the closure member lockable are inserted into the main body of the connector.
- the connector according to claim 4 can also take up the intake duct and pressure duct leading to the neighboring hydraulic pump.
- the coupling piece, including its Blade elements can be designed as a one-piece blade wheel according to claim 5.
- the coupling piece according to claim 6 can be made as a hollow shaft and with the free ends of the drive shafts of the hydraulic pumps according to claim 7 by means of a Wedge / groove toothing must be connected.
- the intake ducts leading to the hydraulic pumps can either be used accordingly Claim 8 open into a common suction opening in the pre-pressure chamber and in Branch the flow direction above the suction opening to the two hydraulic pumps or it can according to claim 10 for each intake duct separate intake duct openings be provided. Accordingly, the coupling piece according to claim 9 only one of its ends is formed by arranging the blade elements as a blade wheel be or it can be paddle wheel-shaped symmetrically at both ends according to claim 11 be trained.
- Fig. 1 shows an axial section through a first embodiment of the Double pump unit developed according to the invention.
- the double pump unit comprises two hydraulic pumps 1 and 2, which in the present embodiment as Axial piston pumps are designed and enclosed by a housing 35 and 39, respectively are.
- the basic structure of axial piston pumps is well known, so that in the illustrated embodiment, only the cylinder drums 3, 4, Drive shafts 5, 6 and the control discs 7, 8 are shown.
- pistons 9, 10 and 11, 12 are arranged movably and are supported on one each Swashplate, not shown.
- the control discs 7, 8 have a kidney shape trained control channels 13, 14, which are formed in the cylinder drum 3, 4 Cylinder bores 15, 16 or 17, 18 alternately with the intake duct 19 or 20 and connect the pressure channel 21 or 22.
- the drive shafts 5 and 6 of the two Axial piston pumps 1 and 2 are via a coupling piece to be described in more detail 23 non-positively connected.
- One of the two drive shafts 5 or 6 is on its free end, not shown, of a likewise not shown Drive device driven so that those connected to the drive shafts 5 and 6 respectively Cylinder drums 3 and 4 are set in rotation.
- the drive shafts 5 and 6 are still in one on rolling bearings 24 and 25 descriptive connector 26 stored.
- the connector 26 is in illustrated embodiment of a main body 27 with an axial, preferably circular opening 28 which can be closed by a closure part 29.
- the coupling piece 23 has, according to the invention, peripherally arranged blade elements 30, 32 on.
- the blade elements 30, 31 are over the entire circumference of the coupling piece 23 distributed at a uniform radial distance.
- the coupling piece 23 is therefore by the Attachment of the blade elements 30, 31 at one end as a blade wheel or turbine educated.
- the blade elements 30, 31 extend in the manner shown in FIG. 1 Embodiment substantially perpendicular to the axis of the drive shafts 5, 6 of the Hydraulic pumps 1, 2.
- the pressure medium to be pumped by the double pump unit flows through the funnel-shaped intake manifold 32 in the provided according to the invention Pre-pressure chamber 33, in which the hydraulic pumps 1 and 2 operate Rotate blade elements 30, 31 of coupling piece 23.
- the blade elements 30, 31 cause a pre-compression of the print medium, so that to be promoted Pressure medium is fed into the intake ducts 19, 20 under a pre-pressure.
- the two intake channels 19 and 20 open into one common intake port opening 34 into the pre-pressure chamber 33.
- the intake ducts 19 and 20 each branch off one of the two hydraulic pumps 1 and 2.
- the intake duct 20 through the Main body 27 of the connecting piece 26 is guided below the sectional plane of FIG. 1 and passed through the closure member 29 so that it is the control channels 14 of the Control disc 8 reached.
- the pressure channel 21 of the hydraulic pump 1 is through the Main body 27 of the connector 26 guided, while the pressure channel 22 of the Hydraulic pump 2 both through the main body 27 and through the closure part 29 is passed through.
- the direction of flow of the pressure medium is through corresponding arrows marked.
- the closure part 29 is designed so that the Coupling piece 23 together with the blade elements 30, 31 by means of the Closure part 29 closable opening 34 in the main body 27 of the Connector 26 can be inserted axially. This facilitates the assembly of the Double pump unit considerably.
- the assembly can be carried out in the following steps: First, the main body 27 of the connector 26 is connected to the housing 35 of the hydraulic pump 1. The coupling piece 23 with the blade elements 30, 31 is then inserted through the opening 34. It is particularly advantageous if the coupling piece 23 is designed as a hollow shaft which has a spline / groove toothing 38 on its inner diameter, which engages in a corresponding spline / groove toothing on the free end 36 of the drive shaft 5 of the hydraulic pump 1. The opening 34 in the main body 27 of the connecting piece 26 can then be closed by means of the closure part 29.
- the second hydraulic pump 2 can subsequently be attached to the connecting piece 26, the free end 37 of the drive shaft preferably likewise having a spline / groove toothing which engages in the corresponding spline / groove toothing 38 on the inside diameter of the coupling piece 23.
- the two-part design of the connector 26 with a one-piece Main body 27 and the closure part 29 therefore enables fluidic Favorable guidance of the intake ducts 19, 20 and quick assembly with little Construction costs.
- the one-piece construction of the main body 27 of the connecting piece 26 offers in addition, other significant advantages. So the overall length and weight of the Double pump unit can be significantly reduced compared to known training and largely leak-free can be achieved since there are no seals to the outside required are.
- the outside surface of the main body 27 of the connector 26 stands for the attachment of further units, e.g. the controller, setting elements or for Connection thread and the like. Available without restriction. Inside the main body 27 additional cylinder bores, oil guide bores, threads etc. can be integrated become.
- Fig. 2 shows a further embodiment of the double pump unit according to the invention.
- the components already described with reference to FIG. 1 are included Matching reference numerals, so that there is a related description unnecessary.
- the suction channels 19 and 20 in separate Intake channel openings 50, 51 into the pre-pressure chamber 33.
- the coupling piece 33 has blade elements 52, 53 and 54, 55 at both ends, which, as in the case of Embodiment according to FIG. 1 at radially uniform intervals in the manner of a Paddle wheel or a turbine are arranged circumferentially on the coupling piece 33.
- FIG. 1 In the exemplary embodiment according to FIG.
- each intake duct 19 or 20 is therefore a separate one blade wheel or turbine consisting of blade elements 52, 53 or 54, 55, assigned, which causes a pre-compression of the pressure medium to be conveyed and the pressure medium under a pre-pressure in the respective intake duct 19 or 20 feeds.
- the distribution on the intake channels 19 and 20 is therefore already in the Pre-pressure chamber 33.
- the symmetrical embodiment according to FIG. 2 has the advantage of an increased Efficiency for the loading pump consisting of the blade elements 52 to 55, so that an increased admission pressure is available in the intake ducts 19 and 20.
- the symmetrical design of the intake channels has the advantage that the in the drawing right intake duct 20 has a shorter length, which is fluidically advantageous.
- the invention is of course not based on the illustrated embodiments limited.
- the blade elements 30, 31 or 52 to 55 can also be any different be constructed constructively.
- the blade elements can form a turbine be composed parallel to the axial direction of the drive shafts 5 and 6 promotes so that the suction channels 19 and 20 largely without curvatures can be.
- the closure part 29 can also be arranged radially in order to Inserting the coupling piece 33 into the main body 27 of the connecting piece 26 in radial direction.
- the present invention cannot only with an axial piston pump, but also with any other known one hydrostatic pump, especially a radial piston pump, are used.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
Description
- Fig. 1
- einen Schnitt durch ein erstesAusführungsbeispiel der Erfindung;
- Fig. 2
- einen Schnitt durch ein zweites Ausführungsbeispiel der Erfindung.
Zunächst wird der Hauptkörper 27 des Verbindungsstücks 26 mit dem Gehäuse 35 der Hydropumpe 1 verbunden. Sodann wird das Kupplungsstück 23 mit den Schaufelelementen 30,31 durch die Öffnung 34 eingeschoben. Dabei ist es besonders vorteilhaft, wenn das Kupplungsstück 23 als Hohlwelle ausgebildet ist, die an ihrem Innendurchmesser eine Keil/Nut-Verzahnung 38 aufweist, die in eine entsprechende Keil/Nut-Verzahnung am freien Ende 36 der Antriebswelle 5 der Hydropumpe 1 eingreift. Sodann kann mittels des Verschlußteils 29 die Öffnung 34 im Hauptkörper 27 des Verbindungsstücks 26 verschlossen werden. Nachfolgnd kann die zweite Hydropumpe 2 an das Verbindungsstück 26 angefügt werden, wobei vorzugsweise das freie Ende 37 der Antriebswelle ebenfalls eine Keil/Nut-Verzahnung aufweist, die in die entsprechende Keil/Nut-Verzahnung 38 am Innendurchmesser des Kupplungsstücks 23 eingreift.
Claims (11)
- Doppelpumpen-Aggregat mit
zwei Hydropumpen (1, 2) mit koaxial zueinander angeordneten Antriebswellen (5, 6), die mittels eines Kupplungsstücks (23) kraftschlüssig miteinander gekoppelt sind, und
einem das Kupplungsstück (23) zumindest teilweise umschließenden Verbindungsstück (26) , in welchem Ansaugkanäle (19,20) zum Ansaugen des zu fördernden Druckmediums durch die Hydropumpen (1, 2 ausgebildet sind,
dadurch gekennzeichnet, daß das Verbindungsstück (26) eine Vordruckkammer (33) aufweist, in welche die Ansaugkanäle (19, 20) münden, und
daß das Kupplungsstück (23) peripher angeordnete Schaufelelemente (30, 31; 52-55) aufweist, die in der Vordruckkammer (33) rotieren, um das Druckmedium unter einem Vordruck in die Ansaugkanäle (19, 20) einzuspeisen. - Doppelpumpen-Aggregat nach Anspruch 1,
dadurch gekennzeichnet, daß das Verbindungsstück (26) zweiteilig ausgebildet ist und neben einem Hauptkörper (27) ein deckelartiges Verschlußteil (29) aufweist, das so ausgebildet ist, daß das Kupplungsstück (23) mit seinen Schaufelelementen (30, 31; 52-55) durch eine mittels des Verschlußteils (29) verschließbare Öffnung (34) in den Hauptkörper (27) des Verbindungsstücks (26) einführbar ist. - Doppelpumpen-Aggregat nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß das Verbindungsstück (26) desweiteren Druckkanäle (21, 22) zum Abfördern des Druckmediums aufweist. - Doppelpumpen-Aggregat nach Anspruch 2 oder 3 soweit auf Anspruch 2 rückbezogen,
dadurch gekennzeichnet, daß der Ansaugkanal (20) und/oder der Druckkanal (22) einer der beiden Hydropumpen (2) durch das Verschlußteil (29) geführt ist. - Doppelpumpen-Aggregat nach einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet, daß das Kupplungsstück (23) einschließlich seiner Schaufelelemente (30, 31; 52-55) einteilig ausgebildet ist. - Doppelpumpen-Aggregat nach einem der Ansprüche 1 bis 5,
dadurch gekennzeichnet, daß das Kupplungsstück (23) als Hohlwelle ausgebildet ist, die die Enden der Antriebswellen (5, 6) der Hydropumpen (1, 2) hülsenartig umschließt. - Doppelpumpen-Aggregat nach Anspruch 6,
dadurch gekennzeichnet, daß das Kupplungsstück (23) mittels einer Keil/Nut-Verzahnung (38) mit den Antriebswellen (5, 6) der Hydropumpen (1, 2) verbunden ist. - Doppelpumpen-Aggregat nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet, daß die jeweils zu einer der beiden Hydropumpen (1, 2) führenden Ansaugkanäle (19, 20) in einer gemeinsamen Ansaugkanalöffnung (34) in die Vordruckkammer (33) münden und in Flußrichtung oberhalb der Ansaugkanalöffnung (34) verzweigen. - Doppelpumpen-Aggregat nach Anspruch 8,
dadurch gekennzeichnet, daß die Schaufelelemente (30, 31) an einem Ende des Kupplungsstücks (23) im Bereich der Ansaugkanalöffnung (34) vorgesehen sind. - Doppelpumpen-Aggregat nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet, daß die jeweils zu einer der beiden Hydropumpen (1, 2) führenden Ansaugkanäle (19, 20) in getrennten Ansaugkanalöffnungen (50, 51) in die Vordruckkammer (33) münden. - Doppelpumpen-Aggregat nach Anspruch 10,
dadurch gekennzeichnet, daß die Schaufelelemente (52-55) an beiden Enden des Kupplungsstücks (23) jeweils im Bereich einer Ansaugkanalöffnung (50, 51) vorgesehen sind.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19536997 | 1995-10-04 | ||
DE19536997A DE19536997C1 (de) | 1995-10-04 | 1995-10-04 | Doppelpumpe mit Ladepumpe |
PCT/EP1996/003562 WO1997013065A1 (de) | 1995-10-04 | 1996-08-12 | Doppelpumpe mit ladepumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0853726A1 EP0853726A1 (de) | 1998-07-22 |
EP0853726B1 true EP0853726B1 (de) | 2003-11-19 |
Family
ID=7774026
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96928452A Expired - Lifetime EP0853726B1 (de) | 1995-10-04 | 1996-08-12 | Doppelpumpe mit ladepumpe |
Country Status (5)
Country | Link |
---|---|
US (1) | US6022198A (de) |
EP (1) | EP0853726B1 (de) |
JP (1) | JP3736643B2 (de) |
DE (2) | DE19536997C1 (de) |
WO (1) | WO1997013065A1 (de) |
Families Citing this family (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6361282B1 (en) | 1998-06-24 | 2002-03-26 | Brueninghaus Hydromatik Gmbh | Dual pump unit |
DE19828180C2 (de) * | 1998-06-24 | 2000-04-20 | Brueninghaus Hydromatik Gmbh | Doppelpumpen-Aggregat |
DE19910659C2 (de) * | 1999-03-10 | 2003-04-03 | Brueninghaus Hydromatik Gmbh | Hydraulische Kolbenmaschineneinheit |
DE19958829C1 (de) | 1999-11-30 | 2001-08-02 | Mannesmann Ag | Brennstoffzellensystem mit einer Vorrichtung zum Zuleiten von Brennstoff |
GB0016193D0 (en) * | 2000-06-30 | 2000-08-23 | Lucas Industries Ltd | Pumps |
DE20018570U1 (de) * | 2000-10-30 | 2002-03-21 | Liebherr Machines Bulle S A | Hydrostatische Doppelaxialkolbenpumpe |
DE10154723A1 (de) * | 2000-11-10 | 2002-10-31 | Parker Hannifin Corp | Axialkolbenpumpe mit interner Vorverdichtung |
US7278263B1 (en) | 2003-06-27 | 2007-10-09 | Hydro-Gear Limited Partnership | Charge pump for a hydraulic pump |
US7007468B1 (en) | 2003-06-27 | 2006-03-07 | Hydro-Gear Limited Partnership | Charge pump for a hydrostatic transmission |
DE10349599B3 (de) * | 2003-10-24 | 2005-07-07 | Brueninghaus Hydromatik Gmbh | Anschlussblock für eine hydrostatische Kolbenmaschine |
US6973783B1 (en) | 2004-02-27 | 2005-12-13 | Hydro-Gear Limited Partnership | Zero turn drive apparatus |
US7377105B1 (en) | 2004-11-12 | 2008-05-27 | Hydro-Gear Limited Partnership | Dual pump assembly |
US7162870B1 (en) | 2004-11-12 | 2007-01-16 | Hydro-Gear Limited Partnership | Pump assembly |
US7347047B1 (en) | 2004-11-12 | 2008-03-25 | Hydro-Gear Limited Partnership | Pump assembly |
US7726126B1 (en) | 2005-12-21 | 2010-06-01 | Hydro-Gear Limited Partnership | Dual pump apparatus with power take off |
US7257948B1 (en) * | 2005-12-21 | 2007-08-21 | Hydro-Gear Limited Partnership | Dual pump apparatus |
US9010105B1 (en) | 2007-08-01 | 2015-04-21 | Hydro-Gear Limited Partnership | Transmission and engine configuration |
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 |
DE102010045867A1 (de) | 2010-09-17 | 2012-03-22 | Robert Bosch Gmbh | Axialkolbenmaschine |
DE102010045872A1 (de) | 2010-09-17 | 2012-03-22 | Robert Bosch Gmbh | Axialkolbenpumpe |
CN102865206A (zh) * | 2012-10-07 | 2013-01-09 | 四川省宜宾普什驱动有限责任公司 | 一种高速泵 |
DE102019213675A1 (de) * | 2019-09-10 | 2021-03-11 | Robert Bosch Gmbh | Hydrostatische Kolbenmaschineneinheit |
US20230358220A1 (en) * | 2022-05-04 | 2023-11-09 | Caterpillar Inc. | Pump having a flange for mounting an auxiliary pump |
DE102022206873A1 (de) | 2022-07-06 | 2024-01-11 | Robert Bosch Gesellschaft mit beschränkter Haftung | Axialkolbenmaschine |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2910008A (en) * | 1954-12-23 | 1959-10-27 | Bendix Aviat Corp | Pump |
US3202101A (en) * | 1963-07-05 | 1965-08-24 | American Brake Shoe Co | Method and means for preventing cavitation in hydraulic piston and vane pumps |
US3644067A (en) * | 1970-05-25 | 1972-02-22 | Sperry Rand Corp | Power transmission |
FR2268956B1 (de) * | 1974-04-24 | 1977-06-24 | Messier Hispano Sa | |
US4014628A (en) * | 1975-05-15 | 1977-03-29 | Caterpillar Tractor Co. | Supercharged three-section pump |
DE2720134A1 (de) * | 1977-05-05 | 1978-11-16 | Spohr Hans Werner | Vorschaltpumpe |
US4281971A (en) * | 1979-07-31 | 1981-08-04 | Abex Corporation | Inlet inducer-impeller for piston pump |
DE3324583A1 (de) * | 1982-07-07 | 1984-01-12 | Linde Ag, 6200 Wiesbaden | Zweimaschinen-aggregat mit anschluss fuer einen weiteren verbraucher mechanischer energie |
US5183392A (en) * | 1989-05-19 | 1993-02-02 | Vickers, Incorporated | Combined centrifugal and undervane-type rotary hydraulic machine |
DE4225380B4 (de) * | 1992-07-31 | 2004-07-15 | Linde Ag | Hydrostatisches Aggregat mit einer Hauptpumpe und einer Nebenpumpe |
JP3209860B2 (ja) * | 1994-07-14 | 2001-09-17 | 川崎重工業株式会社 | タンデム式斜板形ピストンポンプ |
US5800134A (en) * | 1994-10-24 | 1998-09-01 | Kawasaki Jukogyo Kabushiki Kaisha | Tandem, swash plate pump having drive force take-out mechanism |
-
1995
- 1995-10-04 DE DE19536997A patent/DE19536997C1/de not_active Expired - Fee Related
-
1996
- 1996-08-12 EP EP96928452A patent/EP0853726B1/de not_active Expired - Lifetime
- 1996-08-12 DE DE59610826T patent/DE59610826D1/de not_active Expired - Lifetime
- 1996-08-12 WO PCT/EP1996/003562 patent/WO1997013065A1/de active IP Right Grant
- 1996-08-12 US US09/011,390 patent/US6022198A/en not_active Expired - Lifetime
- 1996-08-12 JP JP51391597A patent/JP3736643B2/ja not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
JP3736643B2 (ja) | 2006-01-18 |
JPH11512800A (ja) | 1999-11-02 |
EP0853726A1 (de) | 1998-07-22 |
WO1997013065A1 (de) | 1997-04-10 |
US6022198A (en) | 2000-02-08 |
DE59610826D1 (de) | 2003-12-24 |
DE19536997C1 (de) | 1997-02-20 |
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