EP1017942B1 - Dispositif de regulation pour pompe hydraulique a cylindree variable, comportant plusieurs consommateurs - Google Patents

Dispositif de regulation pour pompe hydraulique a cylindree variable, comportant plusieurs consommateurs Download PDF

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Publication number
EP1017942B1
EP1017942B1 EP98951462A EP98951462A EP1017942B1 EP 1017942 B1 EP1017942 B1 EP 1017942B1 EP 98951462 A EP98951462 A EP 98951462A EP 98951462 A EP98951462 A EP 98951462A EP 1017942 B1 EP1017942 B1 EP 1017942B1
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EP
European Patent Office
Prior art keywords
control
pressure
line
output
delivery
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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
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EP98951462A
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German (de)
English (en)
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EP1017942A1 (fr
Inventor
Helmut Stangl
Detlef Van Bracht
Mikko Erkkilae
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Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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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
    • 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
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/06—Pressure in a (hydraulic) circuit
    • F04B2205/061—Pressure in a (hydraulic) circuit after a throttle

Definitions

  • the invention relates to a control device for a hydraulic pump, in particular for Control of a construction machine, e.g. B. a backhoe loader.
  • a control device is known from the DE 195 17 974 A1 known.
  • a similar control device is known from DE 33 45 264 A1 out.
  • an adjustable hydraulic pump delivers in a delivery line leading to a consumer.
  • a flow control valve is provided that via a first control line with the delivery line downstream of the metering throttle and via a second control line with the delivery line upstream of the metering throttle connected is.
  • the pressure drop occurring at the metering throttle therefore serves Control of the flow control valve, which the signal pressure for the Controls the delivery volume of the hydraulic pump acting adjustment device.
  • a Power control valve which between the first control line and a Pressure medium tank is arranged.
  • the capacity control valve opens in the opening direction acted upon by the control pressure in the first control line while it is in Closing direction via a measuring spring arrangement from the adjusting device in Dependence on the delivery volume predetermined by the adjusting device Hydraulic pump is applied.
  • a suitable choice of the measuring spring arrangement the hyperbolic characteristic of a given maximum power at least approximate.
  • the control characteristic of the control device is maximized by the Flow control valve determines which the flow of the hydraulic pump on the adjusted by the opening cross section of the metering throttle predetermined value.
  • the capacity control valve speaks if the specified maximum capacity is exceeded on and limits the pressure in the first control line, so that the hydraulic pump swung back and an overload is avoided.
  • the known control devices are also used to control several Suitable for consumers.
  • a power control is required.
  • a power control is required to to avoid overloading the drive motor for the hydraulic pump while it is other consumers, where a power limit becomes an undesirable one Lack of performance leads.
  • a backhoe loader one or more hydraulic tools and a hydraulic travel drive.
  • a hydraulic system for commercial vehicles, in particular for road vehicles known.
  • This includes at least one adjustable Hydraulic pump to supply a consumer.
  • the Hydraulic system includes a flow regulator, through which as a function of a pressure difference signal, which at a measuring orifice in the pressure line to the consumer is tapped, the flow rate is regulated.
  • an adjustable hydraulic pump for Care of at least two in different Flow rates and different operating pressures working consumer is provided that in each of of the hydraulic pump leading to a consumer Delivery line an orifice with delivery dependent Cross-section and at consumers with lower Load pressure a pressure compensator is arranged, according to the respective orifices outgoing control pressure lines to the Feed rate controller.
  • the invention is therefore based on the object of a control device for a to create an adjustable hydraulic pump with which the control of several consumers it is possible to achieve the best possible distribution of power.
  • the object is in connection with the characterizing features of claim 1 solved with the smoothing features.
  • the invention is based on the knowledge that an optimal power distribution can be achieved in that only selected, power-controlled consumers with communicate with the power control valve, while the power control valve from the other consumers are not addressed.
  • the flow control valve is via a pressure change device with all consumers including not power-controlled consumers connected.
  • the highest control pressure the control pressures prevailing in the first control lines are selected and the Flow control valve supplied.
  • On the power control therefore have the solution according to the invention influence only those consumers who actually become one Overload of the drive motor driving the hydraulic pump can lead. For the other consumers will experience a lack of performance due to an unnecessary limit on performance avoided.
  • the first control line via a connecting line with the Power control valve is connected.
  • the connecting line opens into the first Control line of this power-controlled consumer upstream of the first Pressure change device for selecting the control pressure for the flow control valve on.
  • the power-controlled consumer in a construction machine e.g. B. a backhoe loader, can e.g. B. be the drive.
  • each can highest control pressure in the first control lines of the group of power-controlled Consumers are selected by a second pressure change device and one too the power control valve leading connecting line according to claim 3 are fed.
  • a throttle to limit the flow through the power control valve can accordingly Claim 4 .
  • this choke can also be used in each one power-controlled consumer assigned first control line according to claim 5 be arranged.
  • the first and the second pressure change device can consist of a pressure change valve or several pressure exchange valves, nested one behind the other according to claim 6 exist.
  • the second can be particularly advantageous Pressure change device according to claim 7 part of the first Pressure change device.
  • a pressure control valve may be arranged that of the control pressure is controlled in the second control line.
  • the control pressure in the second control line corresponds to the pressure in the delivery line at the outlet of the hydraulic pump upstream the metering chokes. If the output pressure of the hydraulic pump is a predetermined one Exceeds the limit value, the pressure control valve responds and swivels the hydraulic pump back.
  • control device can be used in a particularly advantageous manner Control of a construction machine, in particular a backhoe loader according to claim 9 Finding use. At least the drive of the backhoe loader is on power-controlled consumer.
  • Fig. 1 shows a first embodiment of the control device according to the invention.
  • a adjustable hydraulic pump 1 is driven by a drive unit via a drive shaft 2, z. B. a diesel engine.
  • the hydraulic pump 1 draws over the pressure medium a tank line 3 from a pressure medium tank 4 and promotes the pressure medium in a delivery line 5.
  • the delivery line 5 branches into two separate delivery lines 5a and 5b, which each lead to separate consumers.
  • Delivery lines 5a and 5b each have a metering throttle 6a and 6b.
  • the Metering throttles 6a and 6b are used to set the flow rate for the consumer adjustable.
  • the metering chokes 6a and 6b can, for. B. designed as a hand control be and be arranged in the cab of a construction machine.
  • a generally 7 is used to adjust the delivery volume of the hydraulic pump 1 designated adjusting device.
  • Adjusting device 7 from a first actuating cylinder 8, in which a first actuating piston 9 is arranged movably, in connection with the adjusting unit 10 of the hydraulic motor stands.
  • a second actuating piston 11 in connection, which is arranged movably in a second actuating cylinder 12 and by means of a swing-out spring 13 is acted on so that the hydraulic pump 1 by the Swinging spring 13 is pivoted in the direction of maximum delivery volume.
  • the Hydraulic pump 1 pivoted back towards the minimum displacement.
  • the first actuating cylinder 8 and the second actuating cylinder 12 as well as the first actuating piston 9 and the second actuating pistons 11 can also be structurally combined.
  • a flow control valve 15 is provided to control the flow rate.
  • a first one Control input of the flow control valve 15 is connected via a connecting line 16 a pressure change valve 17 connected.
  • the pressure change valve 17 selects the highest control pressure in two first control lines 18a and 18b, each of one assigned delivery line 5a or 5b downstream of that in the delivery lines 5a and 5b provided metering throttle 6a or 6b via a control input X1 or X2 to the Guide pressure change valve 17.
  • the flow control valve 15 is also a second Control line 19 with the delivery line 5 upstream of the metering throttles 6a and 6b connected.
  • the flow control valve 15 is therefore from the pressure difference of the metering throttle 6a and 6b, which is downstream of the metering valve 6a or 6b have the greatest delivery pressure in each case.
  • the flow control valve 15 is in illustrated embodiment formed as a 3/2-way valve.
  • the two inputs of the Flow control valve 15 are on the one hand via the first control line 19 with the Delivery line 5 and on the other hand via the tank line 20 with the pressure medium tank 4 connected.
  • the Flow control valve 15 sets a control pressure in the connecting line 21, the acts on the cylinder space 14 of the first actuating cylinder 8.
  • the valve body of the flow control valve 15 through the Return spring 22 moved so that the connecting line 21 to the pressure medium tank 4 is ventilated.
  • adjusting device 7 is a pressure control valve 23 arranged, which serves to limit the pressure in the delivery line 5. Once the Delivery pressure in the delivery line 5 at the outlet of the hydraulic pump 1 through Return spring 24 exceeds the maximum pressure that can be specified Adjusting device 7 leading signal pressure line 25 with an increased signal pressure acted upon by the 3/2-way valve formed in the embodiment Pressure control valve 23 is moved to a control position in which the Second control line 19 acted upon delivery pressure directly with the control pressure line 25 connected is. As a result, the hydraulic pump 1 is pivoted back and an overpressure in the delivery line 5 avoided.
  • a throttle chain 26 to the return flow of the pressure medium from the To facilitate cylinder chamber 14 to the pressure medium tank 4.
  • a power control valve 27 is provided.
  • the power control valve 27 is between the first control line 18b connected to the delivery line 5b and the to the pressure medium tank 4 leading tank line 20 is arranged.
  • the power control valve 27 is, on the one hand, due to the control pressure prevailing in the first control line 18b the detour line 28 is acted upon in the opening direction.
  • it will Power control valve 27 via a measuring spring arrangement 29 from the adjusting device 7 in Closing direction applied.
  • the measuring spring arrangement 29 is between the actuating piston 9 and a valve piston of the power control valve 27, not shown in detail. With increasing pressure in the delivery line 5b downstream of the associated Metering throttle 6b, the power control valve 27 is acted upon in the opening direction.
  • the power control valve 27 via the measuring spring arrangement 29 by the Adjustment device 7 is increasingly applied in the closing direction when that Delivery volume of the hydraulic pump 1 reduced.
  • a suitable measuring spring arrangement 29 in particular by nesting several springs with different ones Spring constant, a hyperbolic control characteristic can be almost constant Maximum performance can be simulated.
  • a power-controlled consumer is connected to the delivery line 5b, while the delivery line 5a is connected to a non-power-controlled second consumer. If only the metering throttle 6a is open, however, the metering throttle 6b is closed, the input X2 is depressurized, while the control input X1 first control line 18a sets a control pressure.
  • the pressure change valve 17 connects therefore the first control line 18 with the corresponding control input of the Flow control valve 15 so that the pressure drop in the metering throttle 6a to one constant value is adjusted by the flow control valve 15.
  • the control input X2 and thus the first control line 18b are of the corresponding one Control input of the flow control valve separated. The pressure drop at the metering throttle 6b is therefore without influence on the flow control.
  • the power control valve 27 via the detour line 28 is also not in A control pressure is applied to the opening direction.
  • the power regulation is therefore in not active in this operating state.
  • an implement such. B. in Form a hydraulically actuated excavator bucket. During the pure The power control is therefore switched off in excavator operation and an undesirable one Lack of performance does not occur.
  • control input X1 is depressurized and control input X2 is above the first Control line 18b is acted upon by the delivery pressure in delivery line 5b.
  • the pressure change valve 17 passes the control pressure in the first control line 18b to the Flow control valve 15 during the first connected to the delivery line 5a Control line 18a through the pressure change valve 17 from the flow control valve 15 is separated.
  • the flow rate is controlled by means of the flow rate control valve 15. At If the predetermined maximum power is exceeded, the power control valve 27 responds and connects the first control line 18b to the pressure medium tank via the tank line 20 4.
  • a hydraulic implement can be on the delivery line 5a Construction machine, e.g. B. the hydraulic actuator for the excavator bucket Backhoe loader, be connected, while on the delivery line 5b of the hydraulic Travel drive of the construction machine can be connected.
  • the works Control device according to the invention without power limitation, since the control input X2 is depressurized. Only when the hydraulic travel drive is switched on by opening the Metering throttle 6b, the power control valve 27 is activated and monitors the Power output to the hydraulic travel drive.
  • the hydraulic pump 1 is pivoted back to overload the Hydraulic pump 1 via the shaft 2 driving motor, e.g. B. a diesel engine avoid.
  • the regulation according to the invention therefore makes an optimal one Power distribution to the working device connected to the delivery line 5a and the achieved at the conveyor line 5b connected drive.
  • The is advantageously constructive effort for the control device according to the invention is relatively low. It can the control device known from DE 195 17 974 A1 with minor constructive Modifications are used, so that a special design for the control task according to the invention is not necessary. This will make the Manufacturing costs significantly reduced.
  • a choke 30 in the first control line 18b of the power-controlled consumer be provided.
  • the throttle can also be connected to the power control valve 27 leading connecting line 31 may be arranged.
  • FIG. 2 shows a second exemplary embodiment of the control device according to the invention shown. While the control device shown in FIG. 1 and already described for connecting a power-controlled consumer and a non-power-controlled one Consumer is provided, two can on the control device shown in Fig. 2 power-controlled consumers and two non-power-controlled consumers be connected. Elements already described are the same Provide reference numerals, so that a repetitive description is unnecessary.
  • the delivery line 5 branches in the embodiment shown in FIG a total of four separate delivery lines 5a to 5d.
  • Each conveyor line is 5a to 5d
  • a respective first control line 18a to 18d is assigned, which via control connections X1 to X4 of the control device according to the invention are supplied.
  • power-controlled consumers can be connected, while to the Delivery lines 5a and 5c non-power-controlled consumers can be connected.
  • the first pressure change device becomes the highest control pressure in the first Control lines 18a to 18d are selected.
  • the first pressure change device consists of the pressure swing valve 17 and the two further pressure swing valves 40 and 41.
  • the pressure control valve 41 is the highest control pressure of the two Control lines 18b and 18d selected, which with the delivery lines 5b and 5d are connected to which power-controlled consumers are connected. The on this way, control pressure is preselected via the connecting line 42 Pressure change valve 17 supplied.
  • the pressure change valve 40 By means of the pressure change valve 40, the highest in control pressure prevailing between the two control lines 18a and 18c.
  • the Control lines 18a and 18c are connected to conveyor lines 5a and 5c, on which non-regulated consumers are connected.
  • preselected control pressure is the via a connecting line 43 Pressure change valve 17 supplied, the highest overall control pressure of all first control lines 18a to 18d selects and via the connecting line 16 Flow control valve 15 supplies.
  • the flow control follows on the basis all control pressures in all first control lines 18a to 18d.
  • the pressure change valve 41 also serves as a second pressure change device to the to select the highest control pressure of those first control lines 18b and 18d with the delivery lines 5b and 5d are connected to which power-controlled consumers are connected.
  • the second pressure change device is therefore part of the first Pressure-change device.
  • the highest control pressure of the first control lines 18b and 18d is supplied via the connecting line 31 to the power control valve 27, so that the Power control is only based on the control pressures that Delivery lines 5b and 5d come from which power-controlled consumers are connected.
  • control device can also be used for others power-controlled or non-power-controlled consumers are expanded.
  • control device can also be used for others power-controlled or non-power-controlled consumers are expanded.
  • pressure swing valves in the pressure swing devices are each nested in series, so that a corresponding number of connections are available for a corresponding number of consumers.
  • the power control valve 27 could also in other ways, for. B. as a hyperbola regulator, be trained.

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

Abstract

L'invention concerne un dispositif de régulation pour pompe hydraulique (1) à cylindrée variable, qui présente une soupape de régulation de débit (15) et une soupape de régulation de puissance (27). La soupape de régulation de débit (15) est sollicitée par la pression différentielle entre une première conduite de commande (18b), en liaison avec la conduite d'alimentation (5b) en aval d'un papillon de dosage (6b), et une seconde conduite de commande (19), en liaison avec la conduite d'alimentation (5b) en amont du papillon de dosage (6b). Ladite soupape de régulation de débit régule en fonction de cette pression différentielle la pression de réglage pour un dispositif d'ajustement (7) destiné à ajuster le volume de refoulement de la pompe hydraulique (1). La soupape de régulation de rendement (27) est placée entre la première conduite de commande (18b) et un réservoir de fluide hydraulique (4). La pression de commande régnant dans le première conduite de commande (18b) agit sur la soupape de régulation de puissance (27) dans le sens d'ouverture et le dispositif d'ajustement (7) agit sur la soupape de régulation de puissance (27) par l'intermédiaire d'un système de ressorts de mesure (29) dans le sens de fermeture. Selon l'invention, le dispositif de régulation actionne plusieurs consommateurs dont chacun est relié dans chaque cas à la pompe hydraulique (1) par l'intermédiaire d'une conduite d'alimentation (5 a à 5d) séparée, dans laquelle est placée un papillon de dosage (6a à 6d). Dans chaque cas, une conduite de commande (18a à 18d) est en communication avec la conduite d'alimentation menant au consommateur associé, en amont du papillon de dosage (6a à 6d) associé. Un premier dispositif de changement de pression (17, 40, 41) sélectionne la pression de commande la plus élevée parmi les pressions de commande régnant dans les premières conduites de commande (18a à 18d) et l'achemine jusqu'à la soupape de régulation de débit (15). La soupape de régulation de puissance (27) n'est en communication qu'avec les premières conduites de commande (18b, 18d) de consommateurs à régulation de puissance sélectionnés et les conduites de commande (18a, 18c) des autres consommateurs non régulés en puissance sont séparés de la soupape de régulation de puissance (27).

Claims (9)

  1. Dispositif de régulation pour une pompe hydraulique à cylindrée réglable (1), comportant une vanne de régulation de débit (15) qui règle le débit refoulé par la pompe hydraulique (1) en fonction du fluide sous pression s'écoulant à travers un étranglement de dosage (6b) dans une conduite de refoulement (5b) menant à un dispositif consommateur, la vanne de régulation de débit étant sollicitée par la différence de pression entre une première conduite de commande (18b), qui est en liaison avec la conduite de refoulement (5b) en aval de l'étranglement de dosage (6b), et une deuxième conduite de commande (19) qui est en liaison avec la conduite de refoulement (5b) en amont de l'étranglement de dosage (6b), et cette vanne réglant en fonction de cette différence de pression la pression de commande pour un variateur (7) pour faire varier le volume refoulé de la pompe hydraulique (1), et comportant une vanne de réglage de puissance (27) qui est agencée entre la première conduite de commande (18b) et un réservoir de fluide sous pression (4), la pression de commande dans la première conduite de commande (18b) sollicitant la vanne de réglage de puissance (27) dans le sens de l'ouverture, et le variateur (7) sollicitant la vanne de réglage de puissance (27) via un agencement de ressort de mesure (29) dans le sens de la fermeture,
    caractérisé en ce que, par le dispositif de régulation peuvent être pilotés plusieurs dispositifs consommateurs, qui sont chacun reliés à la pompe hydraulique (1) via une conduite de refoulement séparée (5a-5d) dans laquelle est agencé un étranglement de dosage (6a-6d) respectif réglable, en ce qu'une première conduite de commande (18a-18d) respective est en liaison avec la conduite de refoulement (5a-5d) menant au dispositif consommateur associé en aval de l'étranglement de dosage (6a-6d) associé,
    en ce qu'un premier dispositif de changement de pression (17, 40, 41) choisit respectivement la plus élevée des pressions de commande régnant dans les premières conduites de commande (18a - 18d) et l'amène à la vanne de réglage de régulation de débit (15), et
    en ce que la vanne de réglage de puissance (27) n'est en liaison qu'avec les premières conduites de commande (18b, 18d) de dispositifs consommateurs choisis et réglés en puissance, et les premières conduites de commande (18a, 18c) des autres dispositifs consommateurs non réglés en puissance sont séparés de la vanne de réglage de puissance (27).
  2. Dispositif de régulation selon la revendication 1, caractérisé en ce que la vanne de réglage de puissance (27) est reliée à la première conduite de commande (18b) d'un seul dispositif consommateur réglé en puissance via une conduite de liaison (31) qui débouche dans la première conduite de commande (18b) de ce dispositif consommateur réglé en puissance en amont du premier dispositif de changement de pression (17).
  3. Dispositif de régulation selon la revendication 1, caractérisé en ce que la vanne de réglage de puissance (27) est reliée aux premières conduites de commande (18b, 18d) d'un groupe de plusieurs dispositifs consommateurs réglés en puissance via une conduite de liaison (31), et en ce qu'entre une conduite de liaison (31) menant à la vanne de réglage de puissance (27) et les premières conduites de commande (18b, 18d) des dispositifs consommateurs réglés en puissance, il est prévu un deuxième dispositif de changement de pression (41) qui choisit respectivement la plus élevée des pressions de commande régnant dans les premières conduites de commande (18b, 18d) du groupe des dispositifs consommateurs réglés en puissance et l'amène à la conduite de liaison (31).
  4. Dispositif de régulation selon l'une ou l'autre des revendications 2 et 3, caractérisé en ce qu'un étranglement est agencé dans la conduite de liaison (31) menant à la vanne de réglage de puissance (27).
  5. Dispositif de régulation selon l'une des revendications 1 à 4, caractérisé en ce qu'un étranglement (30 ; 30a, 30b) est agencé dans chaque première conduite de commande (18b, 18d) associée à un dispositif consommateur réglé en puissance.
  6. Dispositif de régulation selon l'une des revendications 1 à 5, caractérisé en ce que le premier dispositif de changement de pression (17, 40, 41) et le second dispositif de changement de pression (41) sont constitués par une vanne de changement de pression ou par plusieurs vannes de changement de pression agencées imbriquées les unes derrière les autres.
  7. Dispositif de régulation selon la revendication 6, caractérisé en ce que le deuxième dispositif de changement de pression (41) fait partie du premier dispositif de changement de pression (17, 40, 41).
  8. Dispositif de régulation selon l'une des revendications 1 à 7, caractérisé en ce qu'entre la vanne de régulation de débit (15) et le variateur (7) est agencée une vanne de réglage de pression (23) qui est pilotée par la pression de commande dans la deuxième conduite de commande (19).
  9. Dispositif de régulation selon l'une des revendications 1 à 8, caractérisé en ce que le dispositif de régulation sert à piloter une machine de construction, en particulier une chargeuse-pelleteuse, avec au moins un appareil de travail hydraulique et un système d'entraínement, l'appareil de travail étant relié à une conduite de refoulement (5a) pour un dispositif consommateur non réglé en puissance et le système d'entraínement étant relié à une conduite de refoulement (5b) pour un dispositif consommateur réglé en puissance.
EP98951462A 1997-09-24 1998-09-24 Dispositif de regulation pour pompe hydraulique a cylindree variable, comportant plusieurs consommateurs Expired - Lifetime EP1017942B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19742157 1997-09-24
DE19742157A DE19742157C2 (de) 1997-09-24 1997-09-24 Regeleinrichtung für eine verstellbare Hydropumpe mit mehreren Verbrauchern
PCT/EP1998/006083 WO1999015792A1 (fr) 1997-09-24 1998-09-24 Dispositif de regulation pour pompe hydraulique a cylindree variable, comportant plusieurs consommateurs

Publications (2)

Publication Number Publication Date
EP1017942A1 EP1017942A1 (fr) 2000-07-12
EP1017942B1 true EP1017942B1 (fr) 2003-06-11

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EP98951462A Expired - Lifetime EP1017942B1 (fr) 1997-09-24 1998-09-24 Dispositif de regulation pour pompe hydraulique a cylindree variable, comportant plusieurs consommateurs

Country Status (5)

Country Link
US (1) US6311489B1 (fr)
EP (1) EP1017942B1 (fr)
CA (1) CA2292417C (fr)
DE (2) DE19742157C2 (fr)
WO (1) WO1999015792A1 (fr)

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DE10219850B3 (de) * 2002-05-03 2004-02-05 Brueninghaus Hydromatik Gmbh Regeleinrichtung mit Grenzwertregelventil
DE10343016B4 (de) * 2003-09-17 2010-08-26 Brueninghaus Hydromatik Gmbh Hydraulisches Steuer- und Stellsystem mit Volumenausgleich
KR100752115B1 (ko) * 2004-12-30 2007-08-24 두산인프라코어 주식회사 굴삭기의 유압펌프 제어시스템
WO2008022672A1 (fr) * 2006-08-21 2008-02-28 Joma-Hydromechanic Gmbh Pompe de circulation
US8621860B2 (en) 2010-10-22 2014-01-07 Cnh America Llc Control system for work vehicle
DE102018210720A1 (de) * 2018-06-29 2020-01-02 Robert Bosch Gmbh Hydrostatischer Fahrantrieb mit Druckabschneidung und Verfahren zum Kalibrieren der Druckabschneidung
DE102018210685A1 (de) * 2018-06-29 2020-01-02 Robert Bosch Gmbh Hydrostatischer Fahrantrieb und Verfahren zur Steuerung des hydrostatischen Fahrantriebes

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DE3410071C2 (de) 1984-03-20 1994-06-01 Bosch Gmbh Robert Hydraulikanlage
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JPH04173433A (ja) 1990-11-06 1992-06-22 Toyota Autom Loom Works Ltd 車両用油圧システム
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CA2292417A1 (fr) 1999-04-01
EP1017942A1 (fr) 2000-07-12
US6311489B1 (en) 2001-11-06
CA2292417C (fr) 2007-11-20
DE19742157C2 (de) 1999-07-01
DE19742157A1 (de) 1999-04-01
WO1999015792A1 (fr) 1999-04-01
DE59808716D1 (de) 2003-07-17

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