EP0954703B1 - Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques - Google Patents

Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques Download PDF

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Publication number
EP0954703B1
EP0954703B1 EP97909271A EP97909271A EP0954703B1 EP 0954703 B1 EP0954703 B1 EP 0954703B1 EP 97909271 A EP97909271 A EP 97909271A EP 97909271 A EP97909271 A EP 97909271A EP 0954703 B1 EP0954703 B1 EP 0954703B1
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EP
European Patent Office
Prior art keywords
valve
control
hydraulic pump
valve sleeve
moment
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97909271A
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German (de)
English (en)
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EP0954703A1 (fr
Inventor
Gerhard Beutler
Hermann Maier
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
Priority claimed from DE19646687A external-priority patent/DE19646687C1/de
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0954703A1 publication Critical patent/EP0954703A1/fr
Application granted granted Critical
Publication of EP0954703B1 publication Critical patent/EP0954703B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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 power or torque control device for at least two adjustable hydraulic pumps with one for each hydraulic pump hydraulic servo control unit for continuous adjustment of the delivery rate accordingly the preamble of claim 1.
  • a generic power or torque control device is e.g. from EP 0149 787 B2 known.
  • the Delivery rate of each hydraulic pump depending on the delivery pressure of the respective hydraulic pump in a discharge pressure line assigned to the hydraulic pump and the control pressures in the control lines provided for each hydraulic pump.
  • the piston area over a hydraulically operated control valve can be acted upon with the delivery pressure or with a Process is connectable.
  • the control valve is actuated by the control pressure in the control line of the corresponding hydraulic pump.
  • Torque valve provided with a valve piston movable in a valve sleeve, the forms a sealing seat with the valve sleeve and its closing force of one Measuring spring arrangement is determined, which is connected to the pump actuator and in Is biased depending on the set flow rate.
  • This moment valve of the two hydraulic pumps connects the control line to the assigned one Hydraulic pump depending on the control pressure in this control line and the Control pressure in the control line of the other hydraulic pump under pre-tensioning the Measuring spring arrangement with the sequence.
  • the characteristic of this known power or torque control device is shown in Fig. 2 as a function of the high pressure pHD in in the discharge pressure line Dependence on the flow rate Q of the associated hydraulic pump illustrated.
  • a ideal performance curve of one of the two hydraulic pumps when the consumer is switched off in the pressure circuit of the other hydraulic pump is 1 characterized.
  • This hyperbolic ideal characteristic curve 1 has constant power the product of flow rate Q and pressure pHD in the high pressure line constant and the curve is therefore hyperbolic.
  • the ideal characteristic curve 1 is replaced by a real characteristic curve 1 ' approximated.
  • the real characteristic curve 1 ' has two linear sections. In each of the linear The closing force of the valve piston of the torque valve is determined by one of the sections determines two individual springs provided in the measuring spring arrangement of the torque valve. In this way, the hyperbolic profile of the ideal characteristic 1 for the sufficiently approximate practical needs.
  • the object is in connection with the characterizing features of claim 1 solved with the generic features.
  • the invention is based on the finding that a considerably improved approximation to the ideal characteristic can be achieved if by the from the delivery pressure second hydraulic pump or the delivery pressures provided in any number other hydraulic pumps derived control pressure or control pressures not only the Valve piston, but also the valve sleeve of the torque valve in a suitable manner is applied.
  • each torque valve for each Control line can on the valve piston of each torque valve for each Control line an associated measuring surface can be provided, which with the control pressure of the each assigned control line in the opening direction of the torque valve is acted upon. Furthermore, according to claim 3, a driving pin on the Pump actuator can be provided in the associated valve sleeve Torque valve for changing the bias of the measuring spring arrangement attacks.
  • valve sleeve adjusting piston in the control line of the other hydraulic pump prevailing control pressure act on a valve sleeve adjusting piston so that the Valve sleeve adjusting piston moves the valve sleeve against a return spring.
  • a Intermediate member may be provided according to claim 6.
  • the contact area between the Valve sleeve actuating piston and the intermediate element can shift the valve sleeve Compensate perpendicular to the direction of movement of the valve sleeve adjusting piston if that Intermediate member is carried with the valve sleeve.
  • the valve sleeve adjusting piston or the intermediate member can Have inclined surface, which is in engagement with the valve sleeve Bolt element attacks.
  • the inclined surface deflects the Direction of movement of the valve sleeve adjusting piston to the direction of movement of the Valve sleeve reached.
  • the Driving pin of the pump actuator as a hollow body, in particular as a hollow cylinder be formed, the valve sleeve adjusting piston or the intermediate piece in the Driver pin of the pump actuator slidably engages and from the driver pin is enclosed. This measure also results in a particularly compact one Structure of the torque valve.
  • the Driving pin in the area of the inclined surface corresponding to a suitable recess Claim 9.
  • FIG. 1 shows a hydraulic circuit diagram which shows the power or Torque control device illustrated schematically in one embodiment. at the exemplary embodiment shown in FIG. Torque control device for controlling two hydraulic pumps 10 and 11. Die
  • the power or torque control device according to the invention is also for Suitable for controlling more than two hydraulic pumps in the same way.
  • the hydraulic pumps 10 and 11 are each driven by a drive shaft 12 and 13 driven a drive unit, not shown.
  • the hydraulic pumps 10 and 11 suck the pressure fluid, e.g. Oil from a pressurized fluid tank 41 via an intake pipe 14 and 15 and deliver the pressure fluid to a delivery pressure line 16 or 17, where it is available for a consumer that can be connected to port B.
  • To the with Outputs B connected to the delivery pressure lines 16 and 17 are preferably via adjustable throttle elements 18 and 19 control lines 20 and 21 connected.
  • adjustable throttle elements 18 and 19 control lines 20 and 21 connected.
  • the control line 20 of the first hydraulic pump 10 is connected to the Input X of the servo control unit 22 of the first hydraulic pump 10 and with the input P2 of the servo control unit 23 of the second hydraulic pump 11.
  • the analog is Control line 21 of the second hydraulic pump 11 with the input X of the servo control unit 23 of the second hydraulic pump and with the input P2 of the servo control unit 22 of the first Hydraulic pump 10 connected.
  • the control pressure prevailing in the control line 20 is in a control valve 25 designed as a pressure compensator with the one in the delivery pressure line 16 prevailing delivery pressure compared. For this, the control valve is over a Connection line 24 connected to the delivery pressure line 16.
  • the control valve 25 is a pressure relief valve 26 is connected downstream to the pressure in the control pressure line 27 to limit.
  • the second hydraulic pump is in the servo control unit 23 11 a control valve 28, which operates in any case as a pressure compensator, which controls the pressure in the control line 21 compares with the delivery pressure in the delivery pressure line 17.
  • a control valve 28 which operates in any case as a pressure compensator, which controls the pressure in the control line 21 compares with the delivery pressure in the delivery pressure line 17.
  • the control valve 28 via a connecting line 29 with the delivery pressure line 17 second hydraulic pump 11 connected.
  • the control valve 28 is also a Pressure relief valve 30 downstream to the pressure in the signal pressure line 50 to limit.
  • the first hydraulic pump 10 is moved in the direction of by a swiveling device 31 maximum delivery rate swung out, while the second hydraulic pump 11 by a Swinging device 32 also in the direction of maximum delivery is swung out.
  • the pivoting device 31 or 32 from a piston 35 or 36 which can be loaded against a spring 33 or 34 Swiveling device 31 or 32 engages the delivery rate of hydraulic pump 10 on one or 11 adjusting pump actuator 37 or 38.
  • Pistons 39 and 40 which can be acted upon hydraulically in the signal pressure line 27 or 50 prevailing signal pressure.
  • the control line 20 or 21 is via a torque valve 42 or 43 with the Pressurized fluid tank 41 connected.
  • the valve piston 44 or 45 of the torque valve 42 or 43 is on the one hand of the control pressure in the control line 20 or 21 respectively assigned hydraulic pump 10 and 11 and on the other hand by the control pressure in the Control line 21 or 20 of the other hydraulic pump 11 or 10 in Direction of opening applied.
  • a measuring spring arrangement 46 or 47 on the valve piston 44 or 45 which in the exemplary embodiment consists of two Individual springs exist, in sections, around the one already explained with reference to FIG. 2 to generate a linear course of the characteristic.
  • the preload of the measuring spring arrangement 46 or 47 is determined by the position of the pump actuator 37 or 38.
  • valve sleeve 48 or 49 is also of the one in the control line 21 or 20 of the other hydraulic pump 11 or 10 prevailing control pressure.
  • FIG. 3 shows, similarly to FIG. 2, the one prevailing in the delivery pressure line 16 Delivery pressure pHD as a function of the delivery rate Q of the first hydraulic pump 10 or 11. If the connected to the delivery pressure line 17 of the second hydraulic pump 11 Consumer has only a low power consumption and therefore the second hydraulic pump 11 is only slightly loaded, the first hydraulic pump 10 is connected to the ideal characteristic curve 1 approximate real characteristic curve 1 'adjusted to an approximately constant power. If the second hydraulic pump 11 has a significant power output, the power output by the first hydraulic pump 10 can be reduced so that the Hydraulic pumps 10 and 11 output total power a predetermined maximum value does not exceed and a drive unit driving the hydraulic pumps 10 and 11 is not overloaded.
  • Torque valve 42 and 43 described with reference to FIGS. 4 and 5.
  • 4 shows a vertical longitudinal section through the torque valve 42
  • Fig. 5 a horizontal longitudinal section through the torque valve 42 shows.
  • the torque valves 42 and 43 are formed in the same way, so that the following description the torque valve 42 is limited.
  • the torque valve 42 includes a valve housing 60, one in the valve housing 60 axially movably arranged valve sleeve 61 and a movable with respect to the valve sleeve 61 Valve piston 62.
  • the valve piston 62 is via a spring plate 63 through the Measuring spring arrangement 46 acted upon in the closing direction.
  • the measuring spring arrangement 46 in the exemplary embodiment consists of two individual springs 64 and 65 arranged one inside the other, which leads to the sectionally linear control characteristic shown in FIG. 3.
  • the preload of the spring assembly 46 is adjustable by means of a spring bolt 66.
  • For the Control line 20 is a first pressure medium connection P1 and for control line 21 is a second pressure medium connection P2 is provided in the valve housing 60.
  • the one with the Control line 20 connected pressure medium connection P1 is via a connection channel 75 connected to a first pressure chamber 67.
  • Pressure chamber 67 with the control pressure prevailing in the control line 20 becomes a first measuring surface 68 with the control pressure prevailing in the control line 20 in Opening direction of the torque valve 42 is applied.
  • the torque valve 46 opens the control line 20 to the Pressure fluid tank 41 out.
  • the stepped bore 71 is via a connecting channel 72 connected to the transverse bore 73 so that the pressure fluid flows into the leakage space 74 can.
  • control line 21 connected to the pressure medium connection P2 is via a Connection channel 76 and via further connection channels 77 and 78 with a second Pressure chamber 79 connected, on which a second measuring surface 80 is formed.
  • the in control pressure prevailing in control line 21 therefore acts on valve piston 72 also in the opening direction of the torque valve 42.
  • control pressure prevailing in the control line 21 does not apply only on the valve piston 62, but also on the valve sleeve 61 to this depending on the control pressure prevailing in the control line 21 against a Return spring 81 and the measuring spring assembly 46 to move axially.
  • the one prevailing in the pressure chamber 82 Control pressure of the second control line 21 thus acts on a valve sleeve actuating piston 83.
  • FIGS. 4 and 5 is the direction of movement of the valve sleeve adjusting piston 83 perpendicular to the Direction of movement of the valve sleeve 61 aligned.
  • the valve sleeve adjusting piston 83 acts on an intermediate member 84, which has a plate-like, has end face 85. At its plate-like, end 85 opposite end, the intermediate member 84 has an inclined surface 86 which engages a bolt element 87 formed on the valve sleeve 61. With a suitable, flat angle of inclination of the inclined surface 87 can, if necessary, a Reduction between the movement of the valve sleeve adjusting piston 83 and the movement the valve sleeve 61 can be reached.
  • the intermediate link 84 is shown in FIG Embodiment within a driving pin 88 designed as a hollow cylinder, which is connected to the pump actuator 37 in a suitable manner.
  • the Driving pin 88 has a recess 89 for receiving the bolt element 87, so that the bolt element 87 is flush with the inclined surface 86 of the intermediate member 84.
  • the valve sleeve adjusting piston 83 is located on its opposite the driving pin 88 End biased by an adjusting spring 100 so that the valve sleeve adjusting piston 83 without 4 by the control pressure prevailing in the control line 21 is pressed at the top. In this way, a reset of the valve sleeve adjusting piston 83 reached.
  • the preload of the actuating spring 100 is achieved by adjusting the spring plate 101 adjustable. This is the adjustment of the spring plate 101 after removal of a housing sleeve 102 accessible from the outside.
  • the pump actuator 3 acts by a horizontal displacement of the driving pin 88 also on the valve sleeve 61.
  • the plate-like conclusion 85 of the Intermediate member 84 ensures that the valve sleeve actuating piston 83 despite the in Fig. 4 horizontal movement of the driving pin 88 in constant engagement with the intermediate link 84 stands. Due to the vertical orientation in Fig. 4 Direction of movement of the valve sleeve adjusting piston 83 perpendicular to the direction of movement of the valve sleeve 61 and the driving pin 88 can shift the valve sleeve 61st through the driving pin 88 on the one hand and through the valve sleeve adjusting piston 83 on the other hand, take place independently of one another.
  • the Torque valve can be designed in many other ways. In particular, it can Torque valve further measuring surfaces for the control lines further from the power or. Have torque control device controlled hydraulic pumps. In corresponding The way is then for each additional hydraulic pump to be connected to the valve sleeve actuating piston 83 a separate pressure chamber for each additional one that can be connected Provide hydraulic pump or there are a corresponding number of valve sleeve actuating pistons 83 to be arranged in parallel.

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

Abstract

L'invention concerne un dispositif de régulation de puissance et de couple pour au moins deux pompes hydrauliques (10, 11) ajustables, qui comprend pour chaque pompe hydraulique (10, 11) un appareil de servo-réglage (22, 23) pour ajuster progressivement le débit. A ce effet, le débit de chaque pompe hydraulique (10, 11) est déterminé en fonction de la pression de refoulement de chacune des pompes hydrauliques (10, 11) régnant dans une conduite de pression de refoulement (16, 17) associée à la pompe hydraulique (10, 11) et des pressions de commande régnant dans les conduites de commande (20, 21) prévues pour chaque pompe hydraulique (10, 11). Il est prévu pour chaque appareil de servo-réglage (22, 23) une soupape de couple (42, 43) avec un piston de soupape (62) déplaçable dans une douille de soupape (61), ledit piston de soupape (62) formant un siège de soupape conjointement avec la douille de soupape (61) et dont la force de fermeture est déterminée par un système de ressort de mesure (46, 47) relié à l'élément de régulation de la pompe (37, 38) et étant précontraint en fonction du débit ajusté. A cet effet, chaque soupape de couple (42; 43) relie à une évacuation (41) la conduite de commande (20, 21) de chaque pompe hydraulique (10; 11) associée en fonction de la pression de commande régnant dans cette conduite de commande (20; 21) et de la pression de commande régnant dans la conduite de commande (21; 20) ou des pressions de commande régnant dans les conduites de commande de chacune des autres pompe(s) hydraulique(s) (11; 10), par précontrainte du système de ressort de mesure (46; 47). D'après un développement prévu selon l'invention, pour une pompe hydraulique (10; 11) déterminée, la pression de commande régnant dans la conduite de commande (21; 20) ou les pressions de commande régnant dans les conduites de commande de chacune des autres pompes (11; 10) agit aussi bien sur le piston de soupape (62) que sur la douille de soupape (61) de la soupape de couple (42; 43) associée à la pompe hydraulique (10; 11) déterminée.

Claims (10)

  1. Système de régulation de puissance ou de couple pour au moins deux pompes hydrauliques réglables (10, 11), comportant un appareil de servocommande hydraulique (22, 23) prévu pour chacune des pompes hydrauliques (10, 11) et destiné au réglage en continu du débit refoulé, dans lequel :
    le débit refoulé de chaque pompe hydraulique (10, 11) est déterminé en fonction de la pression de refoulement de la pompe hydraulique respective (10, 11) dans une conduite de refoulement sous pression (16, 17) associée à la pompe hydraulique (10, 11) et en fonction des pressions de commande dans des conduites de commande (20, 21) prévues pour chaque pompe hydraulique (10, 11),
    chaque appareil de servocommande (22, 23) comprend un dispositif de pivotement (31, 32) qui positionne un organe de positionnement de pompe (37, 38) dans le sens d'un débit refoulé maximal, et un piston (39, 40) qui agit sur l'organe de positionnement de pompe (37, 38) dans le sens d'une réduction du débit refoulé et dont la surface de piston peut être sollicitée par la pression de refoulement via une soupape de commande (25, 28) à actionnement hydraulique ou être reliée à une évacuation (41), et l'actionnement de la soupape de commande (25, 28) s'effectue par la pression de commande dans la conduite de commande (20 ; 21) de la pompe hydraulique respective associée (10 ; 11),
    une soupape à couple (42, 43) est prévue pour chaque appareil de servocommande (22, 23) et comprend un piston de soupape (62) mobile dans une douille de soupape (61) et formant un siège étanche avec la douille de soupape (61) et dont la force de fermeture est déterminée par un agencement à ressort de mesure (46, 47) qui est relié à l'organe de positionnement de pompe (37, 38) et qui est précontraint en fonction du refoulé réglé,
    et chaque soupape à couple (42 ; 43) relie la conduite de commande (20 ; 21) de la pompe hydraulique (10 ; 11) respective associée à l'évacuation (41) en fonction de la pression de commande dans cette conduite de commande (20 ; 21) et de la pression de commande dans la conduite de commande (21 ; 20) ou des pressions de commande dans les conduites de commande de l'autre ou des autres pompe(s) respective(s) (11 ; 10) sous la précontrainte de l'agencement à ressort de mesure (46 ; 47),
    caractérisé en ce que
    pour une pompe hydraulique déterminée (10 ; 11), la pression de commande dans la conduite de commande (21 ; 20) ou les pressions de commande dans les conduites de commande de l'autre ou des autres pompe(s) hydraulique(s) respective(s) (11 ; 10) attaque(nt) aussi bien le piston de soupape (62) que la douille de soupape (61) de la soupape à couple (42 ; 43) associée à la pompe hydraulique déterminée (10 ; 11).
  2. Système de régulation de puissance ou de couple selon la revendication 1, caractérisé en ce qu'il est prévu, sur le piston de soupape (62) de chaque soupape à couple (42, 43) pour chaque conduite de commande (20, 21), une surface de mesure associée (68, 80) qui peut être sollicitée par la pression de commande de la conduite de commande respective associée (20, 21) en direction d'ouverture de la soupape à couple (42, 43).
  3. Système de régulation de puissance ou de couple selon l'une ou l'autre des revendications 1 et 2, caractérisé en ce qu'un goujon entraíneur (88) de l'organe de positionnement de pompe (37, 38) attaque la douille de soupape (61) de la soupape à couple associée (42, 43) pour modifier la précontrainte de l'agencement à ressort de mesure (46, 47).
  4. Système de régulation de puissance ou de couple selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le système de régulation de puissance ou de couple pilote deux pompes hydrauliques réglables (10, 11), et dans la soupape à couple (22 ; 23) d'une pompe hydraulique déterminée (10, 11), la conduite de commande (21 ; 20) de l'autre pompe hydraulique respective (11 ; 10) sollicite un piston de positionnement (83) de la douille de soupape par la pression de commande régnant dans cette conduite de commande (21 ; 20), suite à quoi le piston de positionnement (83) de la douille de soupape déplace la douille de soupape (61) à l'intérieur du carter de soupape (60) à l'encontre d'un ressort de rappel (81) et/ou de l'agencement à ressort de mesure (46 ; 47).
  5. Système de régulation de puissance ou de couple selon la revendication 4, caractérisé en ce que la direction de déplacement du piston de positionnement (83) de la douille de soupape est dirigée sensiblement perpendiculairement à la direction de déplacement de la douille de soupape (61).
  6. Système de régulation de puissance ou de couple selon la revendication 5, caractérisé en ce qu'un organe intermédiaire (84) est prévu entre le piston de positionnement (83) de la douille de soupape et la douille de soupape (61) et est relié par coopération de forces aussi bien au piston de positionnement (83) de la douille de soupape qu'à la douille de soupape (61).
  7. Système de régulation de puissance ou de couple selon l'une ou l'autre des revendications 5 et 6, caractérisé en ce que le piston de positionnement (83) de la douille de soupape ou l'organe intermédiaire (84) comprend une surface inclinée (86) qui attaque un élément de goujon (87) en engagement avec la douille de soupape (61).
  8. Système de régulation de puissance ou de couple selon la revendication 7, caractérisé en ce que le goujon entraíneur (88) est réalisé sous la forme d'un corps creux, et en ce que le piston de positionnement (83) de la douille de soupape ou l'organe intermédiaire (84) s'engage en translation dans le goujon entraíneur (88) de l'organe de positionnement de pompe.
  9. Système de régulation de puissance ou de couple selon la revendication 8, caractérisé en ce que le goujon entraíneur (88) comprend au niveau de la surface inclinée (86) du piston de positionnement de la douille de soupape (61) ou de l'organe intermédiaire (84) un évidement (86) pour permettre un appui de l'élément de goujon (87) contre la surface inclinée (86) du piston de positionnement de la douille de soupape (61) ou de l'organe intermédiaire (84), entouré par le goujon entraíneur (88).
  10. Système de régulation de puissance ou de couple selon l'une quelconque des revendications 4 à 9, caractérisé en ce que le ressort de rappel (81) attaque le côté de la douille de soupape (61) détourné de l'agencement à ressort de mesure (46).
EP97909271A 1996-10-31 1997-09-15 Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques Expired - Lifetime EP0954703B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19645014 1996-10-31
DE19645014 1996-10-31
DE19646687A DE19646687C1 (de) 1996-10-31 1996-11-12 Leistungs- bzw. Momentenregeleinrichtung für mehrere Hydropumpen
DE19646687 1996-11-12
PCT/EP1997/005047 WO1998019069A1 (fr) 1996-10-31 1997-09-15 Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques

Publications (2)

Publication Number Publication Date
EP0954703A1 EP0954703A1 (fr) 1999-11-10
EP0954703B1 true EP0954703B1 (fr) 2002-02-20

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Application Number Title Priority Date Filing Date
EP97909271A Expired - Lifetime EP0954703B1 (fr) 1996-10-31 1997-09-15 Systeme de regulation de puissance et de couple pour plusieurs pompes hydrauliques

Country Status (4)

Country Link
US (1) US6324841B1 (fr)
EP (1) EP0954703B1 (fr)
JP (1) JP4082523B2 (fr)
WO (1) WO1998019069A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102606443B (zh) * 2012-03-19 2015-01-28 北京航空航天大学 一种电磁直接驱动电液伺服泵
DE102013006562A1 (de) * 2013-04-16 2014-10-16 Fresenius Medical Care Deutschland Gmbh Verfahren zur Ermittlung des Druckes in einem extrakorporalen Kreislauf

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2216680A1 (de) 1972-04-07 1973-10-11 Bosch Gmbh Robert Regelvorrichtung fuer zwei gekoppelte pumpen
DE8335902U1 (fr) 1983-12-14 1987-06-04 Brueninghaus Hydraulik Gmbh, 7240 Horb, De
US4613286A (en) * 1984-12-31 1986-09-23 Kabushiki Kaisha Komatsu Seisakusho Constant torque control system for a variable displacement pump or pumps
DE4405234C1 (de) * 1994-02-18 1995-04-06 Brueninghaus Hydraulik Gmbh Vorrichtung zur Summenleistungsregelung von wenigstens zwei hydrostatischen Verstellpumpen
US5567123A (en) 1995-09-12 1996-10-22 Caterpillar Inc. Pump displacement control for a variable displacement pump
US5562424A (en) * 1995-09-12 1996-10-08 Caterpillar Inc. Pump displacement control for a variable displacement pump

Also Published As

Publication number Publication date
JP2001502771A (ja) 2001-02-27
EP0954703A1 (fr) 1999-11-10
US6324841B1 (en) 2001-12-04
JP4082523B2 (ja) 2008-04-30
WO1998019069A1 (fr) 1998-05-07

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