EP1017942A1 - 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

Info

Publication number
EP1017942A1
EP1017942A1 EP98951462A EP98951462A EP1017942A1 EP 1017942 A1 EP1017942 A1 EP 1017942A1 EP 98951462 A EP98951462 A EP 98951462A EP 98951462 A EP98951462 A EP 98951462A EP 1017942 A1 EP1017942 A1 EP 1017942A1
Authority
EP
European Patent Office
Prior art keywords
control
line
control valve
pressure
power
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.)
Granted
Application number
EP98951462A
Other languages
German (de)
English (en)
Other versions
EP1017942B1 (fr
Inventor
Helmut Stangl
Detlef Van Bracht
Mikko Erkkilae
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 Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1017942A1 publication Critical patent/EP1017942A1/fr
Application granted granted Critical
Publication of EP1017942B1 publication Critical patent/EP1017942B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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 controlling a construction machine, for. B. a backhoe loader.
  • a control device is known from DE 195 17 974 AI.
  • a similar control device is shown in DE 33 45 264 AI.
  • an adjustable hydraulic pump delivers into a delivery line that leads to a consumer.
  • An adjustable flow restrictor or metering restrictor is provided in the delivery line, with which the delivery flow is predetermined for the consumer.
  • a delivery flow control valve is provided which is connected via a first control line to the delivery line downstream of the metering throttle and via a second control line to the delivery line upstream of the metering throttle. The pressure drop occurring at the metering throttle therefore serves to control the delivery flow control valve, which regulates the signal pressure for an adjusting device acting on the delivery volume of the hydraulic pump.
  • a power control valve is provided, which is arranged between the first control line and a pressure medium tank.
  • the power control valve is acted upon in the opening direction by the control pressure in the first control line, while in the closing direction it is acted upon by the adjusting device via a measuring spring arrangement depending on the delivery volume of the hydraulic pump predetermined by the adjusting device.
  • the hyperbolic characteristic of a predetermined maximum power can be at least approximately simulated by a suitable choice of the measuring spring arrangement.
  • the control characteristic of the control device is determined by the delivery flow control valve, which regulates the delivery flow of the hydraulic pump to the value specified by the opening cross section of the metering throttle. If the specified maximum output is exceeded, however, the power control valve responds and limits the pressure in the first control line, so that the hydraulic pump is pivoted back and an overload is avoided.
  • the known control devices are also suitable for controlling several consumers.
  • power control is not required in all operating states.
  • one or more hydraulic implements and a hydraulic travel drive are driven in a backhoe loader.
  • the drive power for the excavator bucket is available indefinitely and a power limitation would lead to an undesirable lack of power.
  • the invention is therefore based on the object of providing a control device for an adjustable hydraulic pump, with which the control of a plurality of consumers is possible in such a way that the best possible power distribution is achieved.
  • the invention is based on the knowledge that an optimal power distribution can be achieved in that only selected, power-controlled consumers are connected to the power control valve, while the power control valve is not addressed by the other consumers.
  • the flow control valve is connected to all consumers including the non-power-controlled consumers via a pressure change device.
  • the highest control pressure of the control pressures prevailing in the first control lines is selected in each case and fed to the flow control valve. According to the solution according to the invention, therefore, only those consumers which actually lead to an overload of the drive motor driving the hydraulic pump have an influence on the power control. For other consumers, a lack of performance is avoided through an unnecessary limitation of performance.
  • only one power-controlled consumer can be provided, the first control line of which is connected to the power control valve via a connecting line.
  • 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.
  • the power-controlled consumer in a construction machine, e.g. B. a backhoe, z. B. be the drive.
  • the highest control pressure in the first control lines of the group of power-controlled consumers can be selected by a second pressure change device and fed to a connecting line leading to the power control valve.
  • a throttle for limiting the flow through the power control valve can be provided in the connecting line leading to the power control valve.
  • this choke can also be arranged in each first control line assigned to a power-controlled consumer.
  • the first and the second pressure change device can consist of a pressure change valve or a plurality of pressure change valves nested one behind the other.
  • the second pressure change device can be part of the first pressure change device particularly advantageously.
  • a last pressure change valve compares the highest control pressure of the power-controlled consumers with the highest control pressure of the non-power-controlled consumers and the highest overall control pressure is selected for the control of the flow control valve.
  • a pressure control valve can additionally be arranged according to claim 8, which is controlled by the control pressure 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 of the metering throttles. If the output pressure of the hydraulic pump exceeds a predetermined limit value, the pressure control valve responds and swivels the hydraulic pump back.
  • the control device according to the invention can be used in a particularly advantageous manner for controlling a construction machine, in particular a backhoe loader. At least the drive system of the backhoe loader is a power-controlled consumer.
  • the invention is described in more detail below with reference to the drawing. The drawing shows:
  • Fig. 1 shows a first embodiment of the control device according to the invention.
  • Fig. 2 shows a second embodiment of the control device according to the invention.
  • Fig. 1 shows a first embodiment of the control device according to the invention.
  • An adjustable hydraulic pump 1 is driven by a drive unit, for. B. a diesel engine.
  • the hydraulic pump 1 draws the pressure medium from a pressure medium tank 4 via a tank line 3 and conveys the pressure medium into a delivery line 5.
  • the delivery line 5 branches into two separate delivery lines 5a and 5b, each of which leads to separate consumers.
  • a metering throttle 6a and 6b is provided in each of the separate delivery lines 5a and 5b.
  • the metering restrictors 6a and 6b are adjustable for setting the flow rate for the consumer.
  • the metering chokes 6a and 6b can, for. B. be designed as a hand control and arranged in the cab of a construction machine.
  • An adjusting device is used to adjust the delivery volume of the hydraulic pump 1.
  • the adjusting device 7 consists of a first adjusting cylinder 8, in which a first adjusting piston 9 is movably arranged, which is connected to the adjusting unit 10 of the hydraulic motor.
  • a second actuating piston 11 With the adjusting unit 10 of the hydraulic motor 1 there is also a second actuating piston 11, which is movably arranged in a second actuating cylinder 12 and is actuated by means of a pivoting spring 13 such that the hydraulic pump 1 is pivoted out by the pivoting spring 13 in the direction of maximum delivery volume.
  • the hydraulic pump 1 is pivoted back in the direction of the minimal displacement volume.
  • the first actuating cylinder 8 and the second actuating cylinder 12 as well as the first actuating piston 9 and the second actuating piston 11 can also be structurally combined.
  • a flow control valve 15 is provided to control the flow rate.
  • a first control input of the flow control valve 15 is connected to a pressure change valve 17 via a connecting line 16.
  • the pressure change valve 17 selects the highest control pressure in two first control lines 18a and 18b, each of which from an assigned delivery line 5a or 5b downstream of the metering throttle 6a or 6b provided in the delivery lines 5a and 5b via a control input XI or X2 to the Guide pressure change valve 17.
  • the flow control valve 15 is also connected via a second control line 19 to the delivery line 5 upstream of the metering throttles 6a and 6b.
  • the flow control valve 15 is therefore controlled by the pressure difference at the metering throttle 6a and 6b, which have the greatest delivery pressure downstream of the metering valve 6a or 6b.
  • the flow control valve 15 is designed in the exemplary embodiment shown as a 3/2-way valve.
  • the two inputs of the flow control valve 15 are connected via the first control line 19 on the one hand to the delivery line 5 and on the other hand via the tank line 20 to the pressure medium tank 4.
  • a control pressure is set in the connecting line 21, which acts on the cylinder chamber 14 of the first cylinder 8 Stellzy.
  • the valve body of the flow control valve 15 is displaced by the return spring 22 so that the connecting line 21 to the pressure medium tank 4 is vented.
  • a pressure control valve 23 is arranged between the flow control valve 15 and the cylinder space 14 of the adjusting device 7, which serves to limit the pressure in the delivery line 5.
  • the control pressure line 25 leading to the adjusting device 7 is acted upon by an increased control pressure by the pressure control valve 23 in which is designed as a 3/2-way valve in the exemplary embodiment a control position is shifted in which the second control line 19 charged with the delivery pressure is connected directly to the control pressure line 25.
  • a throttle chain 26 is located between the actuating pressure line 25 and the tank line 20 in order to facilitate the backflow of the pressure medium from the cylinder chamber 14 to the pressure medium tank 4.
  • a power control valve 27 is provided.
  • the power control valve 27 is arranged between the first control line 18b connected to the delivery line 5b and the tank line 20 leading to the pressure medium tank 4.
  • the power control valve 27 is acted upon on the one hand by the control pressure prevailing in the first control line 18b via the detour line 28 in the opening direction.
  • the power control valve 27 is acted upon by the adjusting device 7 in the closing direction via a measuring spring arrangement 29.
  • 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.
  • the power control valve 27 is increasingly acted upon in the closing direction by the adjusting device 7 via the measuring spring arrangement 29 when the delivery volume of the hydraulic pump 1 decreases.
  • a suitable measuring spring arrangement 29 in particular by nesting several springs with different spring constants, a hyperbolic control characteristic can be simulated of an almost constant maximum power.
  • control device The functioning of the control device according to the invention is described in more detail below.
  • a power-controlled consumer is connected to the delivery line 5b, while a non-power-controlled second consumer is connected to the delivery line 5a. If only the metering throttle 6a is open, but the metering throttle 6b is closed, the input X2 is depressurized, while a control pressure is established at the control input XI of the first control line 18a.
  • the pressure change valve 17 therefore connects the first control line 18 to the corresponding control input of the flow control valve 15, so that the pressure drop in the metering throttle 6a is regulated to a constant value by the flow control valve 15.
  • the control input X2 and thus the first control line 18b are separated from the corresponding control input of the flow control valve. The pressure drop at the metering throttle 6b is therefore without influence on the flow control.
  • the power control valve 27 Since the control input X2 is depressurized, the power control valve 27 is also not subjected to a control pressure in the opening direction via the detour line 28. The power control is therefore not active in this operating state.
  • an implement such. B. in the form of a hydraulically operated excavator bucket. The power control is therefore switched off during the pure excavator operation and an undesirable lack of performance does not occur.
  • the control input XI is depressurized and the control input X2 is acted upon by the delivery pressure in the delivery line 5b via the first control line 18b.
  • the control pressure in the first control line 18b reaches the delivery flow control valve 15 via the pressure change valve 17, while the first control line 18a connected to the delivery line 5a is separated from the delivery flow control valve 15 by the pressure change valve 17.
  • the flow control valve 27 responds and connects the first control line 18b to the pressure medium tank 4 via the tank line 20 the pressure in the second control line 19 is applied, so that the signal pressure in the signal pressure line 25 is increased and the adjusting device 7 swings the hydraulic pump 1 back towards a lower displacement volume until the predetermined maximum output is again undershot.
  • a hydraulic implement of a construction machine e.g. B. the hydraulic actuating device for the backhoe of a backhoe loader, while the hydraulic line drive of the construction machine can be connected to the delivery line 5b.
  • the control device operates 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 is the power control valve 27 activated and monitors the power output to the hydraulic travel drive. When the predetermined maximum power is exceeded, the hydraulic pump 1 is pivoted back in order to overload the motor driving the hydraulic pump 1 via the shaft 2, for. B.
  • the regulation according to the invention therefore achieves an optimal power distribution between the implement connected to the delivery line 5a and the travel drive connected to the delivery line 5b.
  • the design effort for the control device according to the invention is advantageously relatively low.
  • the control device known from DE 195 17 974 AI with minor structural modifications can be used, so that a special design is not necessary for the control task according to the invention. This significantly reduces manufacturing costs.
  • a throttle 30 can be provided in the first control line 18b of the power-controlled consumer.
  • the throttle can also be arranged in the connecting line 31 leading to the power control valve 27.
  • FIG. 2 shows a second exemplary embodiment of the control device according to the invention. While the control device shown in FIG. 1 and already described is provided for connecting a power-controlled consumer and a non-power-controlled consumer, two can be used on the control device shown in FIG power-controlled consumers and two non-power-controlled consumers can be connected. Elements which have already been described are provided with the same reference numerals, so that a repetitive description is unnecessary.
  • the delivery line 5 branches into a total of four separate delivery lines 5a to 5d.
  • Each of the separate delivery lines 5a to 5b is assigned a separate metering throttle 6a to 6d, so that the metering of the delivery flow for the consumers connected to the delivery lines 5a to 5d can be individually dimensioned by the operator.
  • Each delivery line 5a to 5d is assigned a first control line 18a to 18d, which are supplied to the control device according to the invention via control connections XI to X4.
  • Power-controlled consumers can be connected to the feed lines 5b and 5d, while non-power-controlled consumers can be connected to the feed lines 5a and 5c.
  • the highest control pressure that prevails in the first control lines 18a to 18d is selected in a first pressure change device.
  • the first pressure change device consists of the pressure change valve 17 and the two further pressure change valves 40 and 41. With the pressure change valve 41, the highest control pressure of the two control lines 18b and 18d is selected, which are connected to the delivery lines 5b and 5d, to which power-controlled consumers are connected .
  • the control pressure preselected in this way is supplied to the pressure change valve 17 via the connecting line 42.
  • the highest control pressure prevailing in the two control lines 18a and 18c is selected by means of the pressure change valve 40.
  • the control lines 18a and 18c are connected to delivery lines 5a and 5c, to which non-power-controlled consumers are connected.
  • the control pressure preselected in this way is fed via a connecting line 43 to the pressure change valve 17, which selects the highest overall control pressure of all the first control lines 18a to 18d and feeds it to the flow control valve 15 via the connecting line 16.
  • the flow control therefore follows on the basis of all control pressures in all first control lines 18a to 18d.
  • the pressure change valve 41 also serves as a second pressure change device in order to select the highest control pressure of those first control lines 18b and 18d which are connected to the delivery lines 5b and 5d to which power-controlled consumers are connected.
  • the second pressure change device is thus part of the first pressure change device.
  • the highest control pressure of the first control lines 18b and 18d is supplied to the power control valve 27 via the connecting line 31, so that the power control takes place only on the basis of those control pressures which are from Delivery lines 5b and 5d come to which power-controlled consumers are connected.
  • control device can also be expanded for further power-controlled or non-power-controlled consumers.
  • corresponding pressure change valves are to be provided in the pressure change devices, which 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. be designed as a hyperbola controller.

Landscapes

  • 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).
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 true EP1017942A1 (fr) 2000-07-12
EP1017942B1 EP1017942B1 (fr) 2003-06-11

Family

ID=7843480

Family Applications (1)

Application Number Title Priority Date Filing Date
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)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19953170B4 (de) * 1999-11-04 2004-08-12 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung und Ventilblock für eine Leistungsregelvorrichtung
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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DE3345264A1 (de) * 1983-12-14 1985-06-27 Brueninghaus Hydraulik Gmbh, 7240 Horb Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe
DE3410071C2 (de) 1984-03-20 1994-06-01 Bosch Gmbh Robert Hydraulikanlage
DE3628370A1 (de) 1986-08-21 1988-02-25 Beilhack Maschf Martin Hydraulikanlage fuer nutzfahrzeuge, insbesondere strassenfahrzeuge
JPH04173433A (ja) 1990-11-06 1992-06-22 Toyota Autom Loom Works Ltd 車両用油圧システム
JPH0599126A (ja) * 1991-10-07 1993-04-20 Komatsu Ltd 可変容量型油圧ポンプの容量制御装置
DE19517974A1 (de) * 1995-05-16 1996-11-21 Brueninghaus Hydromatik Gmbh Verschiebbare hydraulische Leistungs- bzw. Momentenregeleinrichtung

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Also Published As

Publication number Publication date
CA2292417A1 (fr) 1999-04-01
EP1017942B1 (fr) 2003-06-11
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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