EP0745189B1 - Dispositif de regulation du debit total d'au moins deux pompes hydrostatiques a cylindree variable - Google Patents

Dispositif de regulation du debit total d'au moins deux pompes hydrostatiques a cylindree variable Download PDF

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Publication number
EP0745189B1
EP0745189B1 EP95908254A EP95908254A EP0745189B1 EP 0745189 B1 EP0745189 B1 EP 0745189B1 EP 95908254 A EP95908254 A EP 95908254A EP 95908254 A EP95908254 A EP 95908254A EP 0745189 B1 EP0745189 B1 EP 0745189B1
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EP
European Patent Office
Prior art keywords
pressure
variable displacement
pumps
control unit
working
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
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EP95908254A
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German (de)
English (en)
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EP0745189A1 (fr
Inventor
Mikko Erkkilae
Karl-Heinz Vogl
Günter FERTIG
Felix Zu Hohenlohe
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Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
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Publication date
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Publication of EP0745189A1 publication Critical patent/EP0745189A1/fr
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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
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1205—Position of a non-rotating inclined plate

Definitions

  • the invention relates to a device for total power control of at least two hydrostatic variable pumps according to the preamble of claim 1.
  • Such a device is known for example from DE-PS 42 08 925.
  • the total power control of this known device distributes the total drive power made available by the drive motor between the two variable pumps. Like any power control, it is based on the principle of adjusting the delivery volume of the variable pumps as a function of the working pressure in such a way that the maximum drive torque or, at constant drive speed, the maximum power consumption of the variable pumps remains essentially constant over the entire working range.
  • the working pressure generated by each variable pump acts as a control pressure via a pressure piston and a lever arm of a two-armed pivot lever acted upon by it on the respectively associated control valve.
  • the pressure piston is displaceably arranged in the adjusting piston of the respectively assigned adjusting device designed as an adjusting cylinder and acts on the lever arm in such a way that its lever length is shortened in the sense of a reduction in the delivery volume of the adjusting pump when the adjusting piston is displaced so that the working pressure can increase in the same ratio, how the delivery volume of the variable pump is reduced. In this way, the product of working pressure and delivery volume is kept constant.
  • the counter pressure at each control valve is generated by two adjustable pressure springs, one of which acts directly on the control valve and the other via the lever arm of the swivel lever acted upon by the control pressure.
  • Another control pressure which corresponds to the working pressure generated by the respective other variable pump, acts against the pressure of the compression spring acting on the lever arm.
  • the sum of the setting values of both pressure springs determines the maximum torque of the respective variable pump and corresponds the total drive torque of the drive motor. This torque can be transmitted by each variable pump as long as there is no second control pressure at the associated control valve, ie as long as the other variable pump does not absorb any torque.
  • variable displacement pump With increasing torque consumption of the latter variable displacement pump, the counterpressure at the control valve of the former variable displacement pump, and thus its torque setting, is reduced to a minimum value which occurs when the further control pressure is equal to or greater than the pressure on the Lever arm acting compression spring.
  • the torque absorption of each variable pump is thus limited to the value (setpoint of the individual drive torque) which corresponds to the setting value of the compression spring acting directly on the associated control valve.
  • a higher torque absorption of each of the two variable displacement pumps is possible, namely if the setpoint of the respective individual drive torque is increased by correspondingly changing the setting value of the compression spring acting directly on the respective control valve and, as a result, the setting values of the three remaining compression springs, or if the torque absorption the other variable pump falls below the set value of the compression spring acting directly on the associated control valve.
  • EP-A-0 232 722 shows a control method in which two hydrostatic variable pumps are controlled by a control unit.
  • the delivery volume of the two variable displacement pumps is recorded by the two sensors, while the working pressure in the associated working lines of the two variable displacement pumps is recorded by two pressure sensors.
  • the speed of the drive machine is detected by a speed sensor.
  • the ideal delivery volume settings of the two variable displacement pumps are determined in an optimization process and the delivery volume of the variable displacement pumps is adjusted using their adjustment device. This adjustment in turn changes the output variables, namely the working pressures and the actual delivery volumes of the variable pumps.
  • An optimal setting of the two pumps can be found through several interactive optimization steps.
  • the delivery volumes of the coupled pumps are therefore regulated on the basis of the measured pump pressures.
  • a device for controlling the hydraulic pumps of a construction machine is disclosed in US Pat. No. 5,176,504.
  • the construction machine has a first hydraulic pump and a second hydraulic pump, which are driven by a drive machine.
  • Hydraulic adjustment devices are connected to the first and second hydraulic pumps via a first and a second adjustment valve.
  • a control unit calculates the change in the drive power based on reference values for the permissible drive power for the first and second hydraulic pumps and on the basis of the current drive power of the first and second hydraulic pumps.
  • the control unit calculates the permissible volume flow based on the speed of the prime mover, the outlet pressures in the working lines of the first and second hydraulic pumps and the permissible drive power.
  • the control unit selects the respective smaller value from a predefined flow rate and an allowable flow rate for each hydraulic pump.
  • the control unit then calculates the associated swivel angles for the first and second hydraulic pumps, so that the minimum values determined above on the first and second hydraulic pumps are set accordingly.
  • the sum of the permissible reference services remains constant.
  • DE-A-42 08 925 relates to a power control device for two variable displacement pumps, each with a control device that can be pressurized with pressure, an associated power control valve, which is acted upon by a first control pressure corresponding to the working pressure of the variable displacement pump to be adjusted against a pressure difference in the direction of the control position, in which the Actuation pressure is controlled in the direction of reduced variable pump delivery volume along a hyperbolic control curve.
  • the pressure difference results from a spring arrangement counterpressure counteracting the first control pressure and the working pressure of the other variable pump and falls from a maximum value to a minimum value as the latter increases.
  • the spring arrangement comprises a first and a second compression spring, the first compression spring being set to a force corresponding to the minimum value and the second compression spring to a force corresponding to the difference between the maximum value and the minimum value of the pressure difference, and the Actuate the first compression spring with its adjusting force and the second compression spring with a force that decreases with increasing second control pressure.
  • the setpoints of the individual drive torques are specified in a very simple manner by means of the setpoint setting device, the electronic control unit dividing the setpoint value stored in its memory part, which preferably corresponds to the total drive torque of the drive motor, in accordance with the setpoint specification and by controlling the electrical control elements, which are preferably designed as force-controlled proportional magnets Control signals that match the given Correspond to setpoints, adjust the control valves to the corresponding back pressures and thus determine the maximum torque of each variable pump.
  • the time-consuming and comparatively imprecise setting of four compression springs required by the prior art is eliminated.
  • the device according to the invention has a considerably simpler structure than the device known from the prior art, which requires the compression springs, the swivel levers, the pressure pistons which can be displaced in the actuating pistons of the actuating devices, and the hydraulic control lines for the further control pressures which counteract the counterpressures.
  • the electronic control unit which is preferably designed as a microcomputer, the electrical control elements, the measuring transducers, which are preferably designed as inductive displacement sensors that detect the respective position of the actuating devices, and the electrical signal lines are easy to install, easy to maintain, enable uncomplicated troubleshooting and overall more precise total power control.
  • An actuating piston 9 is arranged displaceably in each actuating cylinder 7, 8 and is coupled via a piston rod 10 to an actuator 11 or 12 of the respective variable pump 1 or 2.
  • the pressure chambers 13 of the actuating cylinders 7 are each connected via an actuating pressure line 14 to the working line 3 assigned to the respective variable pump 1 or 2.
  • a pressure line 15 leads from each of these working lines 3 to the pressure chambers 13 of the actuating cylinders 8, in each of which a pressure spring 16 is arranged, which, possibly supported by the working pressure removed from the respective working line 3 via the respective pressure line 15, via the piston 9 ,
  • the piston rod 10 and the actuator 12 acts on the swash plate of the variable displacement pump 1 or 2 in the direction of the maximum delivery volume.
  • the piston surfaces of the actuating pistons 9 in the actuating cylinders 7 facing away from the piston rods 10 are larger than those of the actuating pistons 9 arranged in the actuating cylinders 8, so that working pressure which is generated during the operation of the variable displacement pumps 1, 2 via the actuating pressure lines 14 in the pressure chambers 13 of the actuating cylinders 7 builds up as a control pressure, the swash plate of the respective variable displacement pump 1, 2 is adjusted in the direction of the minimum delivery volume via the piston 9 and the piston rod 10.
  • One adjustable stop 17 each in the pressure chambers 13 of the actuating cylinders 7 serves to limit the maximum delivery volume of the variable displacement pumps 1, 2 to different values.
  • One control valve 18 each is arranged in the control pressure lines 14 and divides them into a control pressure line section 19, 20 leading to the respective working line 3 or to the respective control cylinder 7.
  • Each Control valve 18 is designed as a continuously adjustable 3/2-way valve and has two working connections to the signal pressure line sections 19 and 20 as well as a working connection to a relief line 21 leading to the tank 5, into which a leak oil line 22 of the respective variable displacement pump 1 or 2 opens . In the starting position shown in FIG. 1, the work connection to the signal pressure line section 19 is blocked, while the remaining work connections are open.
  • a control pressure line 23 leads to a control connection of the associated control valve 18 and enables its adjustment in the direction of an end position in which the working connections to the signal pressure line section 20 and the relief line 21 are open and the remaining work connection is blocked.
  • the device for total power control of the two variable pumps 1, 2 comprises two electrical control elements 24, two measuring sensors 25, an electronic control unit 26 and a setpoint adjustment device 27 assigned to the latter.
  • the electrical control elements 24 are designed as force-controlled proportional magnets and are each assigned to one of the control valves 18 for the purpose of generating a counter pressure counteracting the control pressure. They are each connected to the electronic control unit 26 via a control signal line 28.
  • the transducers 25 are designed as inductive displacement transducers, which are assigned to the piston rod 10 of the respective actuating cylinder 7 for the purpose of detecting the respectively set delivery volume of the variable pumps 1, 2 and are connected to the electronic control unit 26 via a signal line 29.
  • the electronic control unit 26 is designed as a microcomputer, in the memory part of which the characteristic curve KL g shown in FIG. 2 is stored.
  • this characteristic curve represents the working pressure p as a function of the delivery volume V of a variable displacement pump, it is below as a torque characteristic curve due to its characteristic curve for the torque or power control designated.
  • both variable pumps 1, 2 and thus their torque characteristic curves are identical, so that only one of these characteristic curves is stored in the memory part of the microcomputer 26.
  • the area pxV under the torque characteristic curve KL g is constant for each delivery volume V or for each working pressure p and in the present exemplary embodiment is equal to the total drive torque of the drive motor 6.
  • the point P on the torque characteristic curve KL g denotes the transition from the so-called starting area (vertical section of KL g ) to the control range (hyperbolic section of KL g ), and its ordinate value corresponds to the target value of the counterpressure at the control valve 18, which is assigned to the variable pump 1 or 2, which transmits or is to transmit the total drive torque.
  • the ordinate value of point P thus also corresponds to the maximum torque that this variable displacement pump can transmit, ie in the present case the total drive torque of the drive motor 6.
  • the nominal value of the back pressure at the control valve assigned to the other variable displacement pump is set to zero in order to prevent that this variable pump overloads the drive motor 6 by driving the consumer connected to it.
  • the setpoint sum of these two counterpressure setpoints and thus the sum of the torques of both variable pumps 1, 2, which must not be greater than the total drive torque of the drive motor 6, is also stored in the memory part of the microcomputer 26 and can be setpoint values of any size by means of the setpoint adjustment device be divided.
  • the function of the device according to the invention is as follows: Both adjustment pumps 1, 2, which are set to maximum delivery volume by the compression springs 16, are driven by the drive motor 6 at the same speed.
  • the setpoint adjustment device 27 With the setpoint adjustment device 27, the setpoint sum of the counterpressure setpoints for the two control valves 18, which is stored in the microcomputer 26 and corresponds to the total drive torque of the drive motor 6, is divided according to the desired operating mode and thus each variable pump 1, 2 receives the maximum torque that it can generate. specified, for example for variable pump 1 60% and for variable pump 2 40% of the total drive torque.
  • the microcomputer 26 sets for both variable displacement pumps 1, 2 the torque characteristic curves corresponding to the predetermined back pressure setpoints, ie those characteristic curves whose transitions from their vertical sections to their hyperbolic sections are identified by points P 1 and P 2 , whose ordinate values denote correspond to the specified back pressure setpoints.
  • the microcomputer 26 sets the characteristic curves KL corresponding to the predetermined back pressure setpoints in the exemplary embodiment described here by lowering the hyperbolic section from KL g to the points P 1 , P 2 ; however, other possibilities are also conceivable, such as, for example, selecting from a set of characteristic curves which includes all the characteristic curves corresponding to the possible distributions of the setpoint sum.
  • the microcomputer 26 now processes each of these two predetermined setpoints into a corresponding control signal and outputs this to the proportional magnet 24 of the respectively associated control valve 18, which generates a corresponding counter pressure.
  • variable pumps 1, 2 are set to the maximum delivery volume.
  • both variable pumps 1, 2 load the drive motor 6 with the maximum torque to which they are set and in this way together with the total drive torque that the drive motor 6 applies.
  • the respective control valve 18 responds in accordance with the control pressure and regulates the actuating pressure applied to the associated actuating device in the direction of reducing the delivery volume of the associated variable displacement pump along the hyperbolic section of the respective torque characteristic curve KL 1 or KL 2 .
  • the sensors 25 record the respective position of the actuating pistons 9 of the actuating cylinders 7 and thus the delivery volume of the respectively assigned variable displacement pumps 1 and 2 and generate corresponding signals.
  • the electronic control unit 26 picks up these signals and uses them to determine for each variable pump 1, 2 that working pressure p which, on the associated torque characteristic curve KL 1 or KL 2, corresponds to the delivery volume V detected by the respective transducer 25.
  • This working pressure p is processed in the microcomputer 26 into a corresponding control signal and output to the associated proportional magnet 24 in order to generate a correspondingly higher back pressure at the respective control valve 18.
  • both variable pumps 1, 2, both individually and together with an increase in the working pressure generated by them are pivoted back to a smaller delivery volume in such a way that the individual drive torques corresponding to the set back pressure setpoints or the total drive torque corresponding to the setpoint total is not exceeded.
  • the setpoint sum stored in the memory part of the microcomputer 26 can also be divided with the setpoint setting device 27 to other than the above-mentioned individual setpoints, so that it is possible, for example, to adjust the variable pump 1 to 100% of the total drive torque, for example to drive the chassis, and accordingly adjust the variable displacement pump 2 to zero percent total drive torque.
  • the variable pump 2 is set to 100% and the variable pump 1 is accordingly set to zero percent total drive torque.
  • the proportional magnets can each be assigned a compression spring, so that the back pressure at each control valve 18 results from the force of the proportional magnet and the adjusting force of this compression spring.
  • the setting force of each of these compression springs can correspond to the setpoint sum of the counterpressure setpoints, and in this case each proportional magnet has an opposite direction of action, one of which corresponds to the direction of action of the control pressure if this control pressure is less than the counterpressure and its setpoint is less than the setpoint sum is, and the other coincides with the direction of action of the compression spring when the control pressure is greater than the counter pressure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

Un dispositif permet de réguler le débit total de plusieurs pompes réglables (1, 2) pourvues chacune d'une soupape (18) de régulation du volume refoulé. Une pression de commande correspondante à la pression de travail des pompes à cylindrée variable est appliquée à l'encontre d'une pression antagoniste aux soupapes de régulation (18) qui réagissent lorsque la pression de commande dépasse la pression antagoniste afin de réguler la pompe à cylindrée variable selon une courbe caractéristique (KL) de couple constant. Afin de pouvoir régler aisément les valeurs nominales des couples individuels d'entraînement et d'éviter que les couples ne dépassent la valeur nominale, une unité électronique de commande (16) est raccordée au capteur de mesure (25) qui mesure les volumes refoulés par les pompes à cylindrée variable. La somme des valeurs nominales des pressions antagonistes, ainsi que les courbes caractéristiques du couple (KL) des pompes à cylindrée variable sont enregistrées dans l'unité électronique de commande (16), qui est pourvue d'un régulateur des valeurs nominales (27) qui répartit la somme des valeurs nominales. L'unité électronique de commande (16) règle les courbes caractéristiques du couple (KL1, KL2), transmet des signaux de commande à un élément de commande associé (24) qui génère les pressions antagonistes correspondant aux valeurs nominales prédéterminées des pressions antagonistes, mesure la pression de travail (p) correspondant au volume refoulé (V) sur la courbe caractéristique du couple (KL1, KL2) au moment où chaque soupape de régulation réagit, transforme cette pression de travail (p) en un signal de commande et le transmet à l'élément de commande qui génère la pression antagoniste.

Claims (4)

  1. Dispositif de régulation de la puissance totale d'au moins deux pompes à cylindrée variable (1, 2) hydrostatiques, entraînées par un moteur d'entraînement (6) commun, refoulant dans une conduite de travail respective (3), par réglage de leur volume de refoulement au moyen chacune d'un dispositif de réglage (7 à 12), pouvant être soumis à une pression de réglage, précontraint en direction du volume de refoulement maximal, avec chacune une soupape de régulation (18), affectée à chaque dispositif de réglage, qui est sollicitée par une pression de commande, correspondant à la pression de travail dans la conduite de travail (3) de la pompe à cylindrée variable (1, 2), à régler par le dispositif de réglage (7 à 12) contre une contre-pression, la soupape de régulation (18) réagissant, lorsque la pression de commande est supérieure à la contre-pression, et réglant l'alimentation en pression de réglage du dispositif de réglage (7 à 12), en direction d'une reduction du volume de refoulement de la pompe à cylindrée variable (1, 2), de manière que le produit de la pression de travail et du volume de refoulement soit constant, caractérisé
    - en ce qu'il est prévu une unité de commande (26) électronique avec un élément de mémoire, dans lequel sont mémorisées, pour les pompes à cylindrée variable (1, 2), des courbes caractéristiques (KL) - pression (p) en fonction du volume de refoulement V - de couples de rotation constants ainsi que la somme des valeurs de consigne des contre-pressions agissant sur les soupapes de régulation (18),
    - en ce que l'unité de commande (26) électronique comporte un dispositif de réglage de valeur de consigne (27) pour la répartition de la somme des valeurs de consigne en valeurs de consigne de grandeur quelconque, affectées à chaque pompe à cylindrée variable, règle la courbe caractéristique (KL1, KL2) correspondante respective, conformément aux valeurs de consigne de contre-pression, données de cette façon, traite chacune de ces valeurs de consigne données en un signal de commande correspondant et délivre ce signal de commande à un élément de commande (24) électrique, correspondant, afin de produire une contre-pression correspondante sur la soupape de régulation (18),
    - en ce que le dispositif de commande (26) électronique est raccordé à des capteurs de valeur de mesure (25), qui enregistrent les volumes de refoulement réglés dans chaque cas des pompes à cylindrée variable (1, 2) et
    - en ce que l'unité de commande (26) électronique détermine, lors de l'intervention de chaque soupape de régulation (18), à l'aide de la courbe caractéristique (KL1 ou KL2) réglée de la pompe à cylindrée variable (1 ou 2) respective, la pression de travail (p) qui correspond, sur cette courbe caractéristique (KL1 ou KL2), au volume de refoulement V, détecté par le capteur de valeur de mesure (25) correspondant, traite ce signal de travail (p) en un signal de commande correspondant et délivre ce signal de commande à l'élément de commande (24) correspondant, afin de produire une contre-pression correspondante sur la soupape de régulation (18).
  2. Dispositif selon la revendication 1, caractérisé en ce que l'unité de commande (26) électronique est un micro-ordinateur.
  3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que les capteurs de valeur de mesure (25) sont des capteurs de distance inductifs, qui détectent la position respective des dispositifs de réglage (4, 7).
  4. Dispositif selon l'une au moins des revendications précédentes, caractérisé en ce que les éléments de commande électriques (24) sont des aimants proportionnels réglés par une force.
EP95908254A 1994-02-18 1995-02-02 Dispositif de regulation du debit total d'au moins deux pompes hydrostatiques a cylindree variable Expired - Lifetime EP0745189B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4405234A DE4405234C1 (de) 1994-02-18 1994-02-18 Vorrichtung zur Summenleistungsregelung von wenigstens zwei hydrostatischen Verstellpumpen
DE4405234 1994-02-18
PCT/EP1995/000382 WO1995022694A1 (fr) 1994-02-18 1995-02-02 Dispositif de regulation du debit total d'au moins deux pompes hydrostatiques a cylindree variable

Publications (2)

Publication Number Publication Date
EP0745189A1 EP0745189A1 (fr) 1996-12-04
EP0745189B1 true EP0745189B1 (fr) 1997-12-29

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Application Number Title Priority Date Filing Date
EP95908254A Expired - Lifetime EP0745189B1 (fr) 1994-02-18 1995-02-02 Dispositif de regulation du debit total d'au moins deux pompes hydrostatiques a cylindree variable

Country Status (5)

Country Link
US (1) US5913663A (fr)
EP (1) EP0745189B1 (fr)
JP (1) JPH09508951A (fr)
DE (2) DE4405234C1 (fr)
WO (1) WO1995022694A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE19538649C2 (de) * 1995-10-17 2000-05-25 Brueninghaus Hydromatik Gmbh Leistungsregelung mit Load-Sensing
US6324841B1 (en) 1996-10-31 2001-12-04 Brueninghaus Hydromatik Gmbh Power- and moment-regulating system for a plurality of hydraulic pumps
EP1055844A1 (fr) * 1999-05-20 2000-11-29 Renault Transmission hydromécanique continue à dérivation de puissance pour véhicule automobile
FR2793850B1 (fr) * 1999-05-20 2005-10-21 Renault Unite hydrostatique a cylindree variable
US20040134189A1 (en) * 2003-01-09 2004-07-15 Brigden Alex L Computer monitored portable hydraulic power generation system
US7481051B2 (en) * 2004-04-08 2009-01-27 Timberjack Inc. Tree feller power management
CN101346549B (zh) * 2005-12-27 2011-05-11 日立建机株式会社 液压作业机的泵控制装置、泵控制方法以及工程机械
US9086143B2 (en) 2010-11-23 2015-07-21 Caterpillar Inc. Hydraulic fan circuit having energy recovery
US11725647B2 (en) * 2021-05-18 2023-08-15 Hamilton Sundstrand Corporation On-demand dual variable displacement positive displacement pumping system

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CN1010794B (zh) * 1986-01-11 1990-12-12 日立建机株式会社 液压泵输入功率控制系统
DE3702000A1 (de) * 1987-01-23 1988-08-04 Hydromatik Gmbh Steuervorrichtung fuer ein hydrostatisches getriebe fuer wenigstens zwei verbraucher
US5428958A (en) * 1987-05-19 1995-07-04 Flutron Ab Electrohydraulic control system
JPH0826552B2 (ja) * 1989-07-27 1996-03-13 株式会社小松製作所 建設機械のポンプ吐出量制御システム
GB2251962B (en) * 1990-11-13 1995-05-24 Samsung Heavy Ind System for automatically controlling an operation of a heavy construction
US5182908A (en) * 1992-01-13 1993-02-02 Caterpillar Inc. Control system for integrating a work attachment to a work vehicle
DE4208925C1 (fr) * 1992-03-19 1993-06-03 Hydromatik Gmbh, 7915 Elchingen, De
US5630317A (en) * 1993-03-26 1997-05-20 Kabushiki Kaisha Komatsu Seisakusho Controller for hydraulic drive machine
EP0695875B1 (fr) * 1993-11-30 2001-06-20 Hitachi Construction Machinery Co., Ltd. Unite de commande pour pompe hydraulique
KR950019129A (ko) * 1993-12-30 1995-07-22 김무 유압식 건설기계의 엔진-펌프 제어장치 및 방법
US5554007A (en) * 1994-10-17 1996-09-10 Caterpillar Inc. Variable displacement axial piston hydraulic unit
US5576962A (en) * 1995-03-16 1996-11-19 Caterpillar Inc. Control system and method for a hydrostatic drive system

Also Published As

Publication number Publication date
WO1995022694A1 (fr) 1995-08-24
JPH09508951A (ja) 1997-09-09
DE4405234C1 (de) 1995-04-06
DE59501169D1 (de) 1998-02-05
EP0745189A1 (fr) 1996-12-04
US5913663A (en) 1999-06-22

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