EP0149787B1 - Dispositif de régulation de débit pour une pompe hydraulique réglable - Google Patents

Dispositif de régulation de débit pour une pompe hydraulique réglable Download PDF

Info

Publication number
EP0149787B1
EP0149787B1 EP84115198A EP84115198A EP0149787B1 EP 0149787 B1 EP0149787 B1 EP 0149787B1 EP 84115198 A EP84115198 A EP 84115198A EP 84115198 A EP84115198 A EP 84115198A EP 0149787 B1 EP0149787 B1 EP 0149787B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
pressure
pump
torque
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
Application number
EP84115198A
Other languages
German (de)
English (en)
Other versions
EP0149787B2 (fr
EP0149787A2 (fr
EP0149787A3 (en
Inventor
Gerhard Beutler
Heinz Berthold
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.)
Brueninghaus Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=25816438&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0149787(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0149787A2 publication Critical patent/EP0149787A2/fr
Publication of EP0149787A3 publication Critical patent/EP0149787A3/de
Application granted granted Critical
Publication of EP0149787B1 publication Critical patent/EP0149787B1/fr
Publication of EP0149787B2 publication Critical patent/EP0149787B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash 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
    • 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
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a flow control device according to the preamble of claim 1.
  • a flow control device of this type is known for example from DE-A-15 28 550 and FR-A-22 11 054.
  • the delivery rate is set solely for the purpose of traversing a specific performance curve as a function of the pump delivery pressure or a control or operating pressure which is synchronous with it.
  • the stroke volume of the pump there is a direct functional relationship between the stroke volume of the pump and the control of the operating pressure which actuates the control valve, which results in low-loss torque control because the torque characteristic is not determined by a throttle system by lowering the operating pressure, but only by changing the Spring preload on the momentary valve, d. H. by designing the measuring spring or the measuring spring set.
  • the relationship applies that the product of the operating pressure and the stroke volume of the pump must be constant.
  • the measure of the stroke volume of a hydraulic pump is the position of the pump actuator which adjusts the pump delivery quantity and which, according to the invention, is connected to the torque valve by means of the spring / measuring spring set.
  • the torque valve is followed by the control valve, which acts as a pressure compensator and primarily serves to adjust the delivery rate.
  • the control valve acts as a pressure compensator and primarily serves to adjust the delivery rate.
  • DE-A-15 28 550 and from DE-A-20 38 968 per se to connect a torque valve to the pump actuator by means of a measuring spring set for the delivery rate control, but there are significant differences between these known configurations and the solution according to the invention .
  • DE-A-15 28 550 there is no torque control, but the pump pressure is set so that the max. Operating pressure does not exceed a certain value.
  • DE-A-20 38 968 discloses a power control device for two or more hydraulic pumps, and moreover the torque valve is not arranged so that it pressurizes the operating pressure control line depending on the pressure in the operating pressure control line and the preload of the measuring spring set Process connects.
  • a torque valve is known per se from FR-A-13 18 661, the spring of which is connected to the pump frame, but this known embodiment relates to a manually adjustable pump, and moreover the torque valve does not become dependent on the pressure in the operating pressure control line controlled.
  • the design and arrangement of the torque valve according to the invention in a flow rate control allows in a further embodiment of the invention that the torque valve can be attached to the hydraulic pump as a separate assembly and a driver pin of the pump actuator on the torque valve to change the bias of the measuring spring / measuring spring set depending on the flow rate setting attacks.
  • Such a torque valve can be used for pumps of different sizes and capacities, these pumps only having to match in the adjustment path for the pump actuator, that is to say, for example, in the swivel angle for adjustable inclined-axis pumps.
  • An expedient embodiment of such a torque valve is characterized in claims 4 and 5.
  • the torque characteristic is determined solely by designing the characteristic of the measuring spring or the measuring spring set
  • a particularly expedient embodiment of the invention results if the stop for the measuring spring measuring spring set can be adjusted from the outside by means of a handle in the torque valve. Due to the externally adjustable measuring spring or measuring spring set, any number of different torque characteristics can be preselected and also set or adjusted during operation, which is particularly advantageous when the pump torque is optimally adapted to the torque of the drive machine driving the pump. A quick adaptation to any application is possible.
  • the stop in the torque valve can expediently be arranged on the end of the valve housing and be detachable for the exchange of the measuring spring / measuring spring set.
  • the torque control device is also suitable as a total control for two or more hydraulic pumps mechanically coupled on the drive side if, according to the invention, the closing element of the torque valve of each pump is acted upon by the sum of the pressure in the operating pressure control line of the individual pump and the pressure in the operating pressure line of the other pump (s) and that each torque valve pressurizes the operating pressure control line of its pump as a function of the total operating pressure and the preload of its measuring spring Process connects.
  • the closing elements of the torque valves have a plurality of measuring surfaces which act in parallel and are each acted upon by the operating pressure of one of the pumps.
  • the hydraulic pump 1 is driven via the shaft 2 by a drive, not shown.
  • the pump actuator consists of a swivel element 3, the swivel angle a of which is proportional to the stroke volume of the hydraulic pump 1.
  • the servo-setting device (not shown in detail) for adjusting the swivel angle ⁇ comprises a spring 4 and a steep piston 5 which can be pressurized, the spring 4 adjusting the hydraulic pump 1 in the direction of the maximum swivel angle ⁇ , that is to say the maximum delivery volume.
  • An actuating piston 6 of the actuating device which can also be functionally combined with the piston 5, takes over the resetting function in the direction of a smaller pivot angle a.
  • the control pressure acting on the piston 6 in the line 7 is removed via a control valve 8 and the line 9 from the delivery pressure line 10 of the hydraulic pump 1.
  • a common pressure relief valve 11 is in series with the control valve 8.
  • the control valve 8 is designed as a pressure compensator and is acted upon on the one hand by the delivery pressure and on the other hand by a control pressure in the operating pressure control line 12, which controls the operating pressure of the hydraulic pump 1 behind a throttle 13 which limits the control flow the operating pressure line 14 decreases after an optionally adjustable flow restrictor 15.
  • a moment valve 16 is acted upon on the one hand by the pressure in the control line 12 and on the other hand by a measuring spring or measuring spring set 17, the pretension of which is determined by the position of the piston 6 or the pump actuator 3.
  • the torque valve 16 can connect the control line 12 to the unpressurized outlet 18.
  • the operating pressure in the control line 12 reaches the value set on the torque valve 16 so that it begins to open, a pressure drop occurs at the control slide of the control valve 8 via the throttle 13.
  • the control slide is moved into the switching position 11 and supplies the piston 6 with Control pressure, so that it strives to adjust the actuator 3 of the hydraulic pump 1 in the direction of smaller flow rates.
  • the measuring spring 17 or the measuring spring set of the torque valve 16 is biased.
  • the spring characteristics of the measuring springs or the measuring spring set are designed such that, depending on the preload, an envelope curve is created in the theoretically desired power hyperbola.
  • a defined swivel angle a corresponds to a defined operating pressure in line 10.
  • the delivery rate setting of the hydraulic pump 1 in the area in which the torque control, that is to say the torque valve 16 has not yet responded is carried out in the usual way via the delivery rate throttle 15 and requires no special explanation.
  • FIG. 2 shows an embodiment of a torque valve 16 in its assignment to the pivotable pump actuator of an inclined-axis axial piston pump.
  • the pivotable actuator has a driver pin 20 projecting into the torque valve 16.
  • the torque valve 16 is designed as a seat valve arranged in a valve housing 21 with a valve cone 22 as a closing element which is acted upon by a measuring spring set 17 formed from the springs 23 and 24.
  • the valve seat for the valve cone 22 is formed on a valve body 25 which is displaceably arranged in the valve housing 21 and on which the driver pin 20 of the pump actuator acts.
  • the valve body is acted upon by a spring 26 which is supported in the valve housing 21 and holds the valve body 25 in positive engagement with the driver pin 20.
  • the spring 23 of the measuring spring set 17 is supported on a stop 27 and the spring 24 on an adjusting screw 28 in the stop 27.
  • the stop 27 is screwed into the end of the valve housing 21. Due to the rotational position of the stop 27, the preload of the measuring spring set 17 and thus the position of the desired torque characteristics and the response point of the torque valve 16 can be adjusted.
  • the stop 27 has a handle 29. The course of the torque characteristics or the spring characteristic can be done by changing the bias of the spring 24 with the help of the adjusting screw 28.
  • the pressure in the operating pressure control line 12 acts through the channel 30 in the valve body 25 on the closing member 22 against the force of the measuring spring set 17.
  • the width of the The valve seat determines the effective measuring surface on the closing element 22 for the pressure in the line 12. If the force exerted on the measuring surface by the pressure in the line 12 exceeds the prestressing force of the measuring spring set 17, the valve cone of the closing element 22 lifts off the valve seat in the valve body 25 and opens the control line 12 to the pressureless outlet, formed by the interior 31 of the valve housing 21 which is fixedly connected to the hydraulic pump, the interior 31 being connected to the depressurized interior 32 of the hydraulic pump.
  • the driving pin 20 moves the valve body 25 in FIG. 2 to the right against the closing member 22 and thus increases the preload of the spring set 17 in accordance with the desired course of the torque characteristic.
  • FIG. 3 shows the control device according to the invention as a total torque control for two hydraulic pumps 33, 34, the drive shafts of which are driven directly or via a corresponding transfer gear 35 (only schematically indicated by a dash) by a common drive machine, not shown.
  • the control devices for the individual pumps correspond to the control device shown in FIG. The same parts are provided with the same reference numerals and are not explained again.
  • Only the torque valves denoted by 16 in FIG. 1 are designed here as total torque valves 36 and differ from the torque valve 16 in that the closing member 22 according to FIG. 4 has an additional measuring surface 37. The operating pressure of the other pump acts on this measuring surface 37 in each case via a control line 38, 39.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (9)

1. Dispositif de régulation de débit pour pompe hydraulique réglable, muni d'un appareil de servo-réglage hydraulique pour le réglage continu du débit de la pompe, dans lequel le réglage du débit est déterminé par la pression de sortie de la pompe et la pression qui règne dans un conduit de pilotage à la pression de fonctionnement, et dans lequel l'appareil de réglage contient un ressort (4) qui agit sur l'organe de réglage de la pompe dans le sens du débit maximum, et au moins un piston qui agit sur l'organe de réglage de la pompe dans le sens d'une réduction de débit, la surface du piston pouvant être placée sous la pression de sortie grâce à une valve de pilotage actionnée hydrauliquement, ou est en communication avec un circuit de décharge. l'actionnement de la valve de pilotage intervenant par la pression qui règne dans le conduit de pilotage de la pression de fonctionnement. caractérisé par le fait qu'on prévoit une valve de couple (16. 36) dont la force de fermeture est déterminée par un ressort étalonné 17, ou un jeu de ressorts étalonné, qui sont reliés fonctionnellement à l'organe de réglage (3) de pompe et qui sont prétendus en fonction du réglage de débit et en ce que la valve de couple (16, 36) fait communiquer le conduit de pilotage (12) de la pression de fonctionnement, avec le circuit de décharge (18) sans pression, en fonction de la pression qui règne dans le circuit de pilotage (12), et de la tension préalable du ressort étalonné (17).
2. Dispositif de régulation selon la revendication 1, caractérisé par le fait que la pression régnant dans le conduit de pilotage (12) de la pression de fonctionnement, qui agit sur la valve de pilotage (8) et la valve de couple (16-36), c'est-à-dire sur leurs organes de fermeture, est prélevée à travers une valve d'étranglement (13) dans le conduit de pilotage qui dérive du conduit de pression de fonctionnement (14) de la pompe (1) et en ce qu'en amont de la dérivation du conduit de pilotage (12), on prévoit une valve d'étranglement de débit le cas échéant réglable dans le conduit de pression de fonctionnement.
3. Dispositif de régulation selon l'une des revendications 1 ou 2, caractérisé par le fait que la valve de couple (16, 36) est fixée en tant que sous-ensemble séparé sur la pompe hydraulique (1) et qu'une tige d'entraînement (20) de l'organe de réglage de la pompe est en prise sur la valve de couple (16, 36) pour changer la tension préalable du ressort étalonné (17), ou du jeu de ressorts étalonné, en fonction du réglage du débit.
4. Dispositif de régulation selon la revendication 3, caractérisé par le fait que la valve de couple (16) est formée d'une soupape à siège dans laquelle l'organe de fermeture (22) en forme de cône de soupape, est sous l'action du ressort étalonné (17), ou du jeu de ressorts étalonné, qui s'appuie d'un côté sur une butée (27) réglable dans le corps de valve (21), et dans laquelle le siège de soupape est disposé dans un corps de soupape (25) qui peut coulisser, sur lequel la tige d'entraînement (20) est en prise.
5. Dispositif de régulation selon la revendication 4, caractérisé par le fait que le corps de soupape (25) est sous l'action d'un ressort qui le maintient en contact mécanique avec la tige d'entraînement (20).
6. Dispositif de régulation selon la revendication 4, caractérisé par le fait que la butée (27) du ressort étalonné, ou du jeu de ressort étalonné, peut être réglée de l'extérieur au moyen d'une manette (29).
7. Dispositif de régulation selon la revendication 4 ou 6, caractérisé par le fait que la butée (27) est disposée au bout du corps de valve (21) et peut être démontée pour le remplacement du ressort étalonné (17), ou du jeu de ressort étalonné.
8. Dispositif de régulation selon l'une des revendications précédentes, réalisant une régulation cumulative pour deux ou plusieurs pompes hydrauliques accouplées en ce qui concerne leur entraînement, caractérisé par le fait que l'organe de fermeture (22) de la valve de couple de chaque pompe (33, 34) est sous la somme de la pression qui règne dans le conduit de pilotage (12) de la pression de fonctionnement des pompes individuelles et de la pression de fonctionnement (14)c>"!: de l'autre pompe, ou des autres pompes et que chaque valve de couple (36) fait communiquer le conduit de pilotage (12) de la pression de fonctionnement de sa pompe avec le circuit de décharge (18) sans pression, en fonction de la pression de fonctionnement cumulée et de la tension préalable de son ressort étalonné (17).
9. Dispositif de régulation selon la revendication 8, caractérisé par le fait que les organes de fermeture des valves de couple présentent plusieurs surfaces de mesure qui agissent en parallèle et sont dans chaque cas sous la pression de fonctionnement de l'une des pompes.
EP84115198A 1983-12-14 1984-12-12 Dispositif de régulation de débit pour une pompe hydraulique réglable Expired - Lifetime EP0149787B2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE8335902U DE8335902U1 (de) 1983-12-14 1983-12-14 Drehmomenten-Regeleinrichtung für eine verstellbare Hydropumpe
DE3345264 1983-12-14
DE19833345264 DE3345264A1 (de) 1983-12-14 1983-12-14 Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe

Publications (4)

Publication Number Publication Date
EP0149787A2 EP0149787A2 (fr) 1985-07-31
EP0149787A3 EP0149787A3 (en) 1985-08-21
EP0149787B1 true EP0149787B1 (fr) 1987-05-06
EP0149787B2 EP0149787B2 (fr) 1991-10-02

Family

ID=25816438

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84115198A Expired - Lifetime EP0149787B2 (fr) 1983-12-14 1984-12-12 Dispositif de régulation de débit pour une pompe hydraulique réglable

Country Status (4)

Country Link
US (1) US4668171A (fr)
EP (1) EP0149787B2 (fr)
JP (1) JPS60147588A (fr)
DE (2) DE8335902U1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017213458A1 (de) 2017-08-03 2019-02-07 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit Leistungsbegrenzung

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3644769A1 (de) * 1986-12-30 1988-07-14 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer eine verstellbare hydrostatische maschine
DE3711050A1 (de) * 1987-04-02 1988-10-20 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen
DE3742111A1 (de) * 1987-04-02 1989-06-29 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen veraenderlichen foerder- bzw. schluckvolumens
DE3711053A1 (de) * 1987-04-02 1988-10-20 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen
JP2578371B2 (ja) * 1989-09-22 1997-02-05 株式会社小松製作所 可変容量ポンプの容量制御装置
DE4020325C2 (de) * 1990-06-26 1995-01-05 Hydrokraft Gmbh Regeleinrichtung für verstellbare Hydropumpen
DE4118869C2 (de) * 1991-06-07 1995-06-29 Hydromatik Gmbh Regelvorrichtung zur Regelung des Verdrängungsvolumens mehrerer hydrostatischer Maschinen
DE4141108A1 (de) * 1991-12-13 1993-06-17 Putzmeister Maschf Einrichtung zur regelung des ausgangsdruckes einer verstellpumpe
DE4202631C2 (de) * 1992-01-30 1995-07-06 Hydromatik Gmbh Axialkolbenmaschine, insbesondere Hydropumpe der Schiefscheibenbauart oder der Schrägachsenbauart, deren Durchsatzvolumen durch eine Einstellvorrichtung einstellbar ist
DE4208925C1 (fr) * 1992-03-19 1993-06-03 Hydromatik Gmbh, 7915 Elchingen, De
US5538401A (en) * 1994-07-05 1996-07-23 Denison Hydraulics Inc. Axial piston pump
KR100212645B1 (ko) * 1994-09-30 1999-08-02 토니헬샴 유압펌프의 토출유량 제어장치
DE19517974A1 (de) * 1995-05-16 1996-11-21 Brueninghaus Hydromatik Gmbh Verschiebbare hydraulische Leistungs- bzw. Momentenregeleinrichtung
JPH0986805A (ja) * 1995-09-25 1997-03-31 Kandenko Co Ltd ケーブルドラムの制動装置
JP4082523B2 (ja) 1996-10-31 2008-04-30 ブルーニンガウス ハイドロマチック ゲゼルシャフト ミット ベシュレンクテル ハフツング 複数の液圧ポンプの出力および／またはトルク調整装置
DE19646687C1 (de) * 1996-10-31 1998-02-12 Brueninghaus Hydromatik Gmbh Leistungs- bzw. Momentenregeleinrichtung für mehrere Hydropumpen
DE19742157C2 (de) * 1997-09-24 1999-07-01 Brueninghaus Hydromatik Gmbh Regeleinrichtung für eine verstellbare Hydropumpe mit mehreren Verbrauchern
DE19831587C2 (de) * 1998-07-14 2000-06-15 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung zur Regelung der hydraulischen Leistung einer Hydropumpe
DE10001826C1 (de) * 2000-01-18 2001-09-20 Brueninghaus Hydromatik Gmbh Vorrichtung zum Regeln der Leistung einer verstellbaren Kolbenmaschine
DE10341331B3 (de) * 2003-09-08 2005-05-25 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung
WO2008022672A1 (fr) * 2006-08-21 2008-02-28 Joma-Hydromechanic Gmbh Pompe de circulation
US8647075B2 (en) * 2009-03-18 2014-02-11 Eaton Corporation Control valve for a variable displacement pump
US9086143B2 (en) 2010-11-23 2015-07-21 Caterpillar Inc. Hydraulic fan circuit having energy recovery
DE102016123160A1 (de) * 2016-11-30 2018-05-30 Schwing Gmbh Großmanipulator mit schnell ein- und ausfaltbarem Knickmast

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1318661A (fr) * 1961-12-27 1963-02-22 Sciper Sa Dispositif de sécurité pour pompes volumétriques
GB1126873A (en) * 1964-09-22 1968-09-11 Sperry Rand Corp Improvements in hydraulic supply and control systems
NL165340C (nl) * 1968-05-09 1981-03-16 Philips Nv Inrichting voor het opwekken van gestimuleerde infraroodemissie met een golflengte van ongeveer 10,6 mu bevattende middelen voor het instand houden van een elektrische ontlading in een gedeeltelijk uit kool- zuurgas bestaand gasmensel.
DE1921298B2 (de) * 1969-04-25 1973-08-23 Hydromatik Gmbh, 7900 Ulm Einrichtung zur regelung der foerdermenge verstellbarer axialkolbenpumpen
DE1922269A1 (de) * 1969-04-29 1970-11-12 Bellows Valvair Kaemper Gmbh Summenleistungsregler
BE757640A (fr) * 1969-10-16 1971-04-16 Borg Warner Systemes hydrauliques, notamment pour la regulation d'une pompea debit variable
US3669570A (en) * 1970-03-09 1972-06-13 Mannesmann Meer Ag Power regulation for fluid machines
US3768928A (en) * 1971-06-01 1973-10-30 Borg Warner Pump control system
DE2141722A1 (de) * 1971-08-20 1973-03-01 Bosch Gmbh Robert Druckregler fuer eine verstellbare pumpe
US3856436A (en) * 1972-12-18 1974-12-24 Sperry Rand Corp Power transmission
DD110684A1 (fr) * 1974-03-20 1975-01-05
US3935707A (en) * 1974-07-22 1976-02-03 General Signal Corporation Hydraulic control system
US3941513A (en) * 1974-09-05 1976-03-02 Parker-Hannifin Corporation Variable displacement pump control assembly
DE2461897A1 (de) * 1974-12-31 1976-07-08 Bosch Gmbh Robert Regeleinrichtung fuer eine pumpe
DE2551088C2 (de) * 1975-11-14 1984-06-28 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zur Mengen- und Druckregelung für Verstellpumpen
US4348159A (en) * 1980-01-07 1982-09-07 Rexnord Inc. Convertible pump servo-valve control
JPS57107407A (en) * 1980-12-25 1982-07-03 Daikin Ind Ltd Construction equipment such as power shovel
DE3213958A1 (de) * 1981-08-21 1983-03-03 Robert Bosch Gmbh, 7000 Stuttgart Elektrohydraulische verstelleinrichtung fuer eine hydrostatische maschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017213458A1 (de) 2017-08-03 2019-02-07 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit Leistungsbegrenzung

Also Published As

Publication number Publication date
EP0149787B2 (fr) 1991-10-02
EP0149787A2 (fr) 1985-07-31
DE3345264A1 (de) 1985-06-27
US4668171A (en) 1987-05-26
EP0149787A3 (en) 1985-08-21
JPS60147588A (ja) 1985-08-03
JPH0526955B2 (fr) 1993-04-19
DE8335902U1 (de) 1987-06-04

Similar Documents

Publication Publication Date Title
EP0149787B1 (fr) Dispositif de régulation de débit pour une pompe hydraulique réglable
EP0826110B1 (fr) Dispositif hydraulique coulissant de regulation de puissance et de couple
DE2343611C2 (de) Vorrichtung zum lastabhängigen Steuern einer hydrostatischen Verstellpumpe
DE1916224B2 (de) Hydrostatisches Getriebe
DE2528094A1 (de) Steuersystem fuer hydrostatische getriebe
DE1653385B2 (de) Vorrichtung zum Konstanthalten des Produktes aus Druck und Hubvolumen bei einer Verdrängerpumpe
DE2813486A1 (de) Regelvorrichtung fuer hydraulikpumpen
EP0465474B1 (fr) Agencement de commande de pompes a liquides epais a deux cylindres
DE1430724C3 (de) Lenksystem für ein Gelenkfahrzeug
DE2755545C2 (de) Hydraulische Hilfskraftlenkeinrichtung für Fahrzeuge
DE3443354A1 (de) Hydraulikanlage
DE3320047C2 (fr)
EP1502027B1 (fr) Dispositif de regulation comprenant une soupape de regulation de valeur limite
DE3323278A1 (de) Regelvorrichtung fuer mehrere aus hydrostatischen getrieben bestehende antriebsaggregate
DE2834420C2 (de) Lenkventil
DE4020325C2 (de) Regeleinrichtung für verstellbare Hydropumpen
DE2854593A1 (de) Hydraulische vorrichtung
EP0890757B1 (fr) Commande hydraulique pour des éléments de couplage débrayables, en particulier pour l'embrayage commandé d'un moteur d'entraínement
DE3711050C2 (fr)
EP0954703B1 (fr) Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques
DE2127506A1 (de) Hydrostatische Antriebseinheit für ein Kraftfahrzeug
AT220488B (de) Hydraulische Steuereinrichtung zum Verstellen der Taumelscheiben in einem hydrostatischen Axialkolbengetriebe, insbesondere für Kraftfahrzeuge
DE19646687C1 (de) Leistungs- bzw. Momentenregeleinrichtung für mehrere Hydropumpen
DE9400234U1 (de) Straßenmarkierungsmaschine mit Drosselvorrichtung zur Beeinflussung des Markierungsstoffauftrages
DE1955886C3 (de) Hydrostatisches Axialkolbengetriebe

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): DE FR GB IT SE

AK Designated contracting states

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19850711

17Q First examination report despatched

Effective date: 19860411

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

ET Fr: translation filed
REF Corresponds to:

Ref document number: 3463555

Country of ref document: DE

Date of ref document: 19870611

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: HYDROKRAFT GMBH

Effective date: 19880205

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

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

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

27A Patent maintained in amended form

Effective date: 19911002

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): DE FR GB IT SE

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

ET3 Fr: translation filed ** decision concerning opposition
ITTA It: last paid annual fee
EAL Se: european patent in force in sweden

Ref document number: 84115198.8

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20031126

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20031202

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20031205

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20031209

Year of fee payment: 20

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20041211

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

EUG Se: european patent has lapsed
EUG Se: european patent has lapsed
PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO