EP0446757B1 - Système hydraulique pour fournir une pompe à débit variable - Google Patents

Système hydraulique pour fournir une pompe à débit variable Download PDF

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Publication number
EP0446757B1
EP0446757B1 EP91103253A EP91103253A EP0446757B1 EP 0446757 B1 EP0446757 B1 EP 0446757B1 EP 91103253 A EP91103253 A EP 91103253A EP 91103253 A EP91103253 A EP 91103253A EP 0446757 B1 EP0446757 B1 EP 0446757B1
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EP
European Patent Office
Prior art keywords
input
output
valve
pump
hydraulic
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
Application number
EP91103253A
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German (de)
English (en)
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EP0446757A1 (fr
Inventor
Donald James Macdonald
James Anton Miller
Derek Malcolm Eagles
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.)
Deere and Co
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Deere and Co
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Publication date
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Publication of EP0446757A1 publication Critical patent/EP0446757A1/fr
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Publication of EP0446757B1 publication Critical patent/EP0446757B1/fr
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/007—Installations or systems with two or more pumps or pump cylinders, wherein the flow-path through the stages can be changed, e.g. from series to parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or filtering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means

Definitions

  • the invention relates to a hydraulic system for supplying at least one first hydraulic function by means of a main pump which is charged by a charge pump, an excess partial liquid flow of the charge pump supplying at least one second hydraulic function.
  • the main pump is preferably a high-pressure pump with an adjustable delivery rate (variable pump), for example an axial piston pump, for supplying a closed hydraulic circuit.
  • variable pump for example an axial piston pump
  • the charge pump it is necessary that the charge pump have a flow rate that is sufficient to satisfy the liquid demand of the variable displacement pump even at a low engine speed.
  • the charge pump's liquid output increases, so that precautions must be taken to discharge excess amounts of liquid that are not absorbed by the main pump.
  • variable displacement pump mainly only pumps a minimal flow of liquid over time, a large part of the liquid is unnecessarily directed back through the circuit to the reservoir. This leads to increased ventilation of the hydraulic fluid and to Loss of performance. In addition, large line cross sections are required to keep the pressure drop low.
  • DE-OS 35 00 310 describes a hydraulic system which has a control pump for supplying load circuits and a feed pump for supplying a supply circuit.
  • the pressure side of the feed pump is also connected to the suction side of the control pump. If the control pump for supplying the load circuit works at full capacity, it requires more pressure fluid than can be provided by the Seise Vietnamese. In this case, a liquid jet pump is activated to ensure that the control pump is supplied.
  • US Pat. No. 4,173,867 shows a hydraulic circuit in which a first pump supplies both a lubricating oil circuit and the charge pump for a variable displacement pump with liquid. If the pressure in the lubricating oil circuit drops, liquid is fed from the outlet of the charge pump to the lubricating oil circuit via a lubricating oil priority valve. This means that the supply of the lubricating oil circuit is given priority over the supply of the variable pump.
  • the object to be achieved with the invention is seen in specifying a hydraulic system of the type mentioned at the outset, in which the supply of a first hydraulic function fed by the main pump is given priority over a second hydraulic function and through which the delivery of excess amounts of liquid can be reduced and Power losses are minimized.
  • a liquid jet pump should be unnecessary.
  • a priority valve is connected to the charge pump, the main pump inlet and the second hydraulic function and optionally excess fluid not used by the main pump directs it from the charge pump to the second hydraulic function and an input of the charge pump.
  • a liquid jet pump for supplying the main pump is unnecessary.
  • the amount of liquid conveyed by the charge pump does not flow back to the reservoir unused, but serves to supply other circuits. This can reduce power losses and aeration of the liquid.
  • the priority valve is usually closed and prefers a liquid supply to the main pump. Depending on an increase in the inlet pressure of the main pump, excess charging fluid is delivered to the lubricating oil circuits through the priority valve from a predeterminable first pressure level. Depending on a further increase in the inlet pressure of the main pump, excess charging liquid is directed both to the lubricating oil circuits and to the inlet of the charging pump from a second pressure level.
  • variable displacement pump 14 which can be driven by a motor, a lubricating oil circuit, such as right and left driveline lubricating oil circuits 16, 18, a lubricating oil circuit 20 for a PTO and a lubricating oil circuit 22 for a pump drive.
  • the variable displacement pump 14 is, for example, an axial piston pump that serves to supply various hydraulic functions 15, such as steering, brakes and control valves, with liquid under pressure.
  • a hydraulic control circuit 28 receives hydraulic fluid from the charge pump 12 and a downstream filter circuit 30 and distributes this to the main pump 14 and the lubricating oil circuit 16-22.
  • the filter circuit 30 contains a filter 32, a check valve 34, (optionally) a strainer 36 and a filter bypass valve 38. Hydraulic fluid is passed through line 44 from the charge pump 12 to the inlet of the valve 38 and to the inlet side of the filter 32.
  • the output side of the filter 32 is connected via a check valve 34 and the lines 46 and 48 to the input of the main pump 14 and via the scanning line 49 to a control chamber which is located on the side of the valve 38 which is also attacked by a return spring.
  • a first outlet of the valve 38 is connected to the line 46 via the (optional) sieve 36.
  • a second outlet of the valve 38 is connected to the collecting container 10 via the line 50.
  • the scan line 54 connects line 44 to the pressure sensitive control port of valve 38.
  • Line 56 connects a third outlet of valve 38 to a pressure sensitive switch 58 which preferably triggers an indicator, such as a light bulb, on the dashboard when line 56 is pressurized.
  • Line 60 connects line 46 to the inlet of valve 40.
  • a first outlet 53 of valve 40 is connected via line 68 to lubricating oil circuits 20 and 22.
  • a second outlet 55 is connected to the lubricating oil circuits 16 and 18 via the orifice 78 and the line 70.
  • Channel 52 connects a third outlet 57 of valve 40 to the inlet of charge pump 12.
  • the inlet pressure of main pump 14 is applied to one end of spool or valve member 41 of valve 40 while the other end of spool or valve member 41 biased by a spring 43 and connected to the line 70 via the diaphragm 76 and the line 74.
  • the oil is drawn through the pre-filter 11 by the charge pump 12. From there it is pumped to the filter circuit 30.
  • the liquid is either passed through the oil filter 32 and the check valve 34, which prevents the connecting lines from leaking when changing the filter, or through the filter bypass valve 38.
  • the switch 58 outputs a display signal at 3.0 bar, which signals that the bypass condition has almost been reached, according to which bypass oil is only permitted when the pressure difference across the filter 32 reaches a value of 5 bar.
  • the bypass oil is passed through a 100 micron sieve 36 and then follows the same path that it would have taken under normal conditions as it passed through the filter 32.
  • the oil then flows to a point from where it flows to the input of the main pump 14 if necessary or, if there is no oil request from the main pump 14, to the boost pressure priority branch valve 40. No oil flows through the valve 40 if the pressure at the inlet of the main pump 14 does not exceed 0.5 bar. From 0.5 bar, the valve 40 adjusts itself so that it directs oil to the lubricating oil circuits 20 and 22. When these lubricating oil circuits reach a pressure of 1.0 bar, the valve 40 opens further and a cooling oil flow is directed to the lubricating oil circuits 16 and 18.
  • the pressure at the valve 40 reaches a value of 1.5 bar, this directs a part of the oil quantity coming from the charge pump 12 and the filter circuit 30 and entering the valve 40 to the channel 52, via which the oil returns to the suction side the charge pump 12 is guided.
  • the spring-loaded side of the slide 41 is connected to the line 70 via a line 74 and an orifice 76. To improve filter usage and cooling, a high proportion of the charging oil should flow through the lubricating oil circuit at maximum engine speed.
  • the charge pump 12 Since the charge pump 12 is oversized with regard to the maximum demand of the main pump 14, a flow rate for the lubricating oil circuit is available at all times. It is also believed that the main pump 14 rarely operates at full capacity, so the amount of oil available to the lubricating oil circuits should be more than sufficient.
  • the bypass function of the boost priority branch valve 40 through which excess oil is returned to the charge pump inlet, is intended to keep the flow rate of unfiltered oil through the oil filter 11 as low as possible. This is desirable in order for the system to operate with a charge pump 12 which is designed for 2.3 l / s at high idling speed and yet only absorbs 1.0 l / s of the unfiltered oil under most operating conditions.
  • the flow rate generated by the charge pump 12 must be sufficient to supply the main pump 14 at full delivery rate.
  • FIG. 2 shows an alternative embodiment of the invention, in which, however, the hydraulic circuit line 64 connects the outlet 59 of the valve 40 ′ via the line 80 and the orifice 81 to the inlet of the charge pump 12. Furthermore, line 62 connects a second inlet 61 of valve 40 'to the outlet of charge pump 12. Valve 40' has a first position in which all connections are blocked, a second position in which inlet 51 is connected to outlet 53 and a third position in which the input 51 is connected to the output 53 and the input 61 is connected to the output 59. Finally, in the embodiment according to FIG. 2, the output 53 is connected to the lines 68 and 70 via the line 66. A check valve 42 is disposed in line 68 to allow one-way fluid flow to functions 20 and 22 and to give priority to flow to functions 16 and 18.
  • charge pump 12 supplies oil to the main pump inlet either through filter 32 or, more likely, through filter bypass valve 38.
  • the boost pressure is likely to exceed 1.5 bar required to transfer excess boost flow through the bypass formed by valve 40 'to the inlet to direct the charge pump 12.
  • the circuit 28 is preferably located approximately equidistant from the main pump inlet and the charge pump inlet, and the bypass line 80 contains a restriction 81 so that the main pump 14 still enjoys priority. If no oil is requested by the main pump 14, the charge flow rate is passed on to the charge pump 12, which contributes to warming up the hydraulic circuit, and to the lubricating oil circuits 16-20.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Fluid Gearings (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Rotary Pumps (AREA)

Claims (11)

  1. Système hydraulique pour l'alimentation d'au moins une première fonction hydraulique (15) par une pompe principale (14) qui est chargée par une pompe de remplissage (12), un flux partiel de liquide excédentaire de la pompe de remplissage (12) alimentant au moins une deuxième fonction hydraulique (16 à 22), caractérisé en ce qu'une soupape de priorité (40, 40') est reliée à la pompe de remplissage (12), à l'entrée de la pompe principale et à la deuxième fonction hydraulique (16 à 22), et elle dirige sélectivement du liquide excédentaire, non sollicité par la pompe principale, de la pompe de remplissage (12) vers la deuxième fonction hydraulique (16 à 22) ou vers une entrée de la pompe de remplissage (12).
  2. Système hydraulique selon la revendication 1, caractérisé en ce que la sortie de la pompe de remplissage (12) est reliée, avec intercalation d'un filtre (32), à l'entrée de la pompe principale (14) et à une entrée (51) de la soupape de priorité (40, 40'), et en ce que la soupape de priorité (40, 40') comporte une première sortie (53), reliée à la deuxième fonction hydraulique (16 à 22), et un obturateur (41, 41'), mobile en fonction de la pression de liquide régnant à l'entrée de la pompe principale (14), qui ferme toutes les entrées et sorties dans une première position et qui relie l'entrée (51) à la première sortie (53) dans une deuxième position.
  3. Système hydraulique selon la revendication 2, caractérisé en ce que l'obturateur (41, 41') est sollicité dans sa première position par un élément de ressort (43), et dans sa deuxième position par la pression de liquide régnant à l'entrée de la pompe principale (14).
  4. Système hydraulique selon la revendication 2 ou 3, caractérisé en ce que la soupape de priorité (40) comporte une deuxième sortie (55) reliée à une troisième fonction hydraulique (16, 18), et en ce que l'obturateur (41) relie, dans une troisième position, l'entrée (51) à la première sortie (53) et/ou à la deuxième sortie (55).
  5. Système hydraulique selon l'une quelconque des revendications 2 à 4, caractérisé en ce qu'un point d'étranglement (78) est prévu dans la conduite de liaison (68) entre la première sortie (53) et la deuxième fonction hydraulique (20, 22), et/ou dans la conduite de liaison (70) entre une deuxième sortie (55) et une troisième fonction hydraulique (16, 18).
  6. Système hydraulique selon l'une quelconque des revendications 3 à 5, caractérisé en ce que le côté de l'obturateur (41, 41') qui est sollicité par l'élément de ressort (43) est relié par l'intermédiaire d'un point d'étranglement (76) à l'entrée de la deuxième ou d'une troisième fonction hydraulique (16, 18 ; 20, 22).
  7. Système hydraulique selon l'une quelconque des revendications 2 à 6, caractérisé en ce que la soupape de priorité (40, 40') comporte une sortie supplémentaire (57, 59) reliée à l'entrée de la pompe de remplissage (12), et en ce que l'obturateur (41, 41') relie, dans une position supplémentaire, l'entrée (51) à la première sortie (53) et/ou à la deuxième sortie (55) et/ou à la sortie supplémentaire (57, 59).
  8. Système hydraulique selon la revendication 2 ou 3, caractérisé en ce que la soupape de priorité (40') comporte une deuxième entrée (61) reliée à l'entrée de la pompe de remplissage (12), et en ce que l'obturateur (41'), dans la deuxième position, relie uniquement la première entrée (51) à la première sortie (53), et, dans une troisième position, relie la première entrée (51) à la première sortie (53) ainsi que la deuxième entrée (61) à la deuxième sortie (55).
  9. Système hydraulique selon l'une quelconque des revendications 2 à 8, caractérisé en ce que la deuxième fonction hydraulique comprend un premier circuit de lubrification (16, 18) et un deuxième circuit de lubrification (20, 22), qui sont respectivement reliés à la première sortie (53) de la soupape de priorité (40, 40') par l'intermédiaire d'une première conduite (70) et d'une deuxième conduite (68), et en ce qu'un clapet antiretour (42) est prévu dans la deuxième conduite (68), lequel empêche un écoulement par la deuxième conduite (68) dans la mesure où la pression dans la première conduite (70) ne dépasse pas une valeur prédéterminable.
  10. Système hydraulique selon l'une quelconque des revendications 2 à 9, caractérisé en ce qu'un point d'étranglement (81) est prévu dans la conduite de liaison (80) entre l'entrée de la pompe de remplissage (12) et la sortie de la soupape de priorité (40, 40') qui est reliée à cette entrée.
  11. Système hydraulique selon l'une quelconque des revendications 1 à 10, caractérisé en ce qu'un filtre (32) et une soupape de dérivation de filtre (38) sont prévus, la soupape de dérivation de filtre (38) faisant contourner le filtre (32) par au moins une partie du flux de liquide lorsque la pression du liquide à l'entrée du filtre dépasse une valeur prédéterminable.
EP91103253A 1990-03-13 1991-03-05 Système hydraulique pour fournir une pompe à débit variable Expired - Lifetime EP0446757B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US492198 1990-03-13
US07/492,198 US5020324A (en) 1990-03-13 1990-03-13 Charge flow priority circuit

Publications (2)

Publication Number Publication Date
EP0446757A1 EP0446757A1 (fr) 1991-09-18
EP0446757B1 true EP0446757B1 (fr) 1994-08-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP91103253A Expired - Lifetime EP0446757B1 (fr) 1990-03-13 1991-03-05 Système hydraulique pour fournir une pompe à débit variable

Country Status (8)

Country Link
US (1) US5020324A (fr)
EP (1) EP0446757B1 (fr)
JP (1) JP3070962B2 (fr)
AT (1) ATE110444T1 (fr)
CA (1) CA2038112C (fr)
DE (1) DE59102593D1 (fr)
ES (1) ES2057630T3 (fr)
MX (1) MX172032B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104533766A (zh) * 2014-12-03 2015-04-22 安徽博一流体传动股份有限公司 一种可带多种变量控制功能的液压柱塞泵
EP3516272B1 (fr) 2016-09-26 2021-12-01 hofer powertrain innovation GmbH Système hydraulique d'alimentation, entre autres pour actionneurs d'embrayage
DE102011115805B4 (de) 2011-10-12 2021-12-09 Robert Bosch Gmbh Hydraulisches System mit einer Hauptpumpe und mit einer Ladepumpe

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE9303680L (sv) * 1993-05-25 1994-11-26 Haakan Ingvast Produktutveckli Vätskeburet system med anordning för avgasning av vätskan
JPH0854058A (ja) * 1994-08-11 1996-02-27 Kanzaki Kokyukoki Mfg Co Ltd 車軸駆動装置
US6182588B1 (en) * 1998-05-01 2001-02-06 Flexi-Coil Ltd. Hydraulic system having boost pump in series with a primary pump and a boost pump drive therefor
ITMO20020332A1 (it) * 2002-11-15 2004-05-16 Studio Tecnico 6M Srl Circuito fluidodinamico per la alimentazione di utenze primarie ed ausiliarie con priorita' predefinite.
US7954317B2 (en) * 2007-12-21 2011-06-07 Deere & Company Hydraulic system
EP3009681A1 (fr) * 2014-10-15 2016-04-20 HILTI Aktiengesellschaft Purge passive et active automatique d'une pompe à eau à amorçage automatique
US9671009B2 (en) 2014-10-22 2017-06-06 Deere & Company Pressure and flow compensated hydraulic system
DE102016001357A1 (de) * 2016-02-06 2017-08-10 Borgwarner Inc. Hydraulikkomponente, Kombination aus Hydraulikkomponenten und hydraulisches System mit mindestens einer solchen Hydraulikkomponente oder Kombination
CN106523456B (zh) * 2016-11-03 2018-01-19 北汽福田汽车股份有限公司 一种混凝土输送泵车及其布料液压系统
DE102017219645A1 (de) 2017-11-06 2019-05-09 Zf Friedrichshafen Ag Ventil, Hydrauliksystem und Kraftfahrzeuggetriebe
DE102020100583A1 (de) * 2020-01-13 2021-07-15 Schwäbische Hüttenwerke Automotive GmbH Fluidversorgungssystem zur Versorgung mehrerer Fluidverbraucher eines Kraftfahrzeugs mit Fluid
DE102021120313A1 (de) * 2021-08-04 2023-02-09 Deere & Company Hydraulische Anordnung und landwirtschaftliches oder industrielles Nutzfahrzeug

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2642804A (en) * 1950-03-31 1953-06-23 Dowty Equipment Ltd Hydraulic power unit
US3131540A (en) * 1961-04-20 1964-05-05 Kopat Ges Fur Konstruktion Ent Hydrostatic drive, particularly for automotive vehicles
US3266424A (en) * 1964-10-27 1966-08-16 Massey Ferguson Inc Fluid system including variable displacement pump
US3588285A (en) * 1968-10-21 1971-06-28 Sunstrand Corp Hydraulic pump
DE2033053A1 (de) * 1970-07-03 1972-01-05 Robert Bosch Gmbh, 7000 Stuttgart Steuereinrichtung für Verdrängerpumpe
US3785157A (en) * 1972-11-24 1974-01-15 Deere & Co Flow control dump valve
US3952511A (en) * 1974-12-30 1976-04-27 Allis-Chalmers Corporation Hydrostatic drive circuit
US3987628A (en) * 1976-03-04 1976-10-26 Deere & Company Charge pump augmenting device
US4173867A (en) * 1978-02-27 1979-11-13 Sundstrand Corporation Transmission
US4255091A (en) * 1979-02-05 1981-03-10 Dike Equipment Corporation Structural unit for hydraulic systems
US4724673A (en) * 1986-06-30 1988-02-16 Vickers, Incorporated Power transmission

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011115805B4 (de) 2011-10-12 2021-12-09 Robert Bosch Gmbh Hydraulisches System mit einer Hauptpumpe und mit einer Ladepumpe
CN104533766A (zh) * 2014-12-03 2015-04-22 安徽博一流体传动股份有限公司 一种可带多种变量控制功能的液压柱塞泵
EP3516272B1 (fr) 2016-09-26 2021-12-01 hofer powertrain innovation GmbH Système hydraulique d'alimentation, entre autres pour actionneurs d'embrayage

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Publication number Publication date
CA2038112A1 (fr) 1991-09-14
JPH04211704A (ja) 1992-08-03
JP3070962B2 (ja) 2000-07-31
DE59102593D1 (de) 1994-09-29
CA2038112C (fr) 1994-08-16
ATE110444T1 (de) 1994-09-15
ES2057630T3 (es) 1994-10-16
EP0446757A1 (fr) 1991-09-18
US5020324A (en) 1991-06-04
MX172032B (es) 1993-11-29

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