EP0954703A1 - 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

Info

Publication number
EP0954703A1
EP0954703A1 EP97909271A EP97909271A EP0954703A1 EP 0954703 A1 EP0954703 A1 EP 0954703A1 EP 97909271 A EP97909271 A EP 97909271A EP 97909271 A EP97909271 A EP 97909271A EP 0954703 A1 EP0954703 A1 EP 0954703A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
hydraulic pump
torque
valve sleeve
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
EP97909271A
Other languages
German (de)
English (en)
Other versions
EP0954703B1 (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

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
    • F04B49/002—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, each with a hydraulic servo control device provided for each hydraulic pump for the continuous adjustment of the delivery rate according to the preamble of claim 1.
  • a generic power or torque control device is e.g. known from EP 0149 787 B2.
  • the delivery quantity of each hydraulic pump is determined as a function of the delivery pressure of the respective hydraulic pump in a delivery pressure line assigned to the hydraulic pump and the control pressures in control lines provided for each hydraulic pump.
  • the servo control unit has a swiveling device which sets a pump actuator in the direction of the maximum flow rate and a piston which acts on the pump actuator in the direction of a flow rate reduction, the piston surface of which can be acted upon by the delivery pressure via a hydraulically actuated control valve or can be connected to a drain.
  • the control valve is actuated by the control pressure in the control line of the corresponding hydraulic pump.
  • a torque valve is provided with a valve piston movable in a valve sleeve, which forms a sealing seat with the valve sleeve and whose closing force is determined by a measuring spring arrangement which is connected to the pump actuator and is biased in dependence on the set delivery rate.
  • This torque valve of the two hydraulic pumps connects the control line of the respectively assigned hydraulic pump as a function of the control pressure in this control line and the control pressure in the control line of the respective other hydraulic pump under pretension of the measuring spring arrangement with the outlet.
  • the closing force of the valve piston of the torque valve is determined by one of two individual springs provided in the measuring spring arrangement of the torque valve.
  • the invention is based on the finding that a considerably improved approximation to the ideal characteristic curve can be achieved if the control pressure or control pressures derived from the delivery pressure of the second hydraulic pump or the delivery pressures of the additional hydraulic pumps provided in any number is not only the Valve piston, but also the valve sleeve of the torque valve is acted upon in a suitable manner.
  • an associated measuring surface can be provided on the valve piston of each torque valve for each control line, which can be acted upon by the control pressure of the respectively assigned control line in the opening direction of the torque valve.
  • a driving pin can be provided on the pump actuator, which engages in the valve sleeve of the associated torque valve to change the bias of the measuring spring arrangement.
  • the control pressure prevailing in the control line of the respective other hydraulic pump can act on a valve sleeve actuating piston such that the valve sleeve actuating piston displaces the valve sleeve against a return spring.
  • valve sleeve adjusting piston it is advantageous if the direction of movement of the valve sleeve adjusting piston is directed essentially perpendicular to the direction of movement of the valve sleeve, since this enables a particularly compact construction of the torque valve.
  • An intermediate member according to claim 6 can be provided between the valve sleeve adjusting piston and the valve sleeve. The contact surface between the valve sleeve adjusting piston and the intermediate member can compensate for the displacement of the valve sleeve perpendicular to the direction of movement of the valve sleeve adjusting piston when the intermediate member is carried along with the valve sleeve.
  • valve sleeve adjusting piston or the intermediate member can have an inclined surface, which is in engagement with the valve sleeve
  • the driver pin of the pump actuator can be designed as a hollow body, in particular as a hollow cylinder, the valve sleeve adjusting piston or the intermediate piece in the
  • Driver pin of the pump actuator slidably engages and is enclosed by the driver pin. This measure also results in a particularly compact one
  • FIG. 1 is a hydraulic circuit diagram of the power or
  • Fig. 3 shows the control characteristic of a performance or Torque control device
  • Fig. 4 is a vertical section through a in the inventive power or. Torque control device used torque valve
  • FIG. 5 shows a horizontal section through a torque valve according to the invention corresponding to FIG. 4.
  • FIG. 1 shows a hydraulic circuit diagram which schematically illustrates the power or torque control device according to the invention using an exemplary embodiment.
  • the power or. Torque control device for controlling two hydraulic pumps 10 and 11.
  • the power or torque control device according to the invention is also 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 from a drive unit, not shown.
  • the hydraulic pumps 10 and 11 draw the pressure fluid, for example oil, from a pressure fluid tank 41 via an intake line 14 and 15, respectively, 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.
  • Control lines 20 and 21 are connected to the outputs B connected to the delivery pressure lines 16 and 17 via preferably adjustable throttle elements 18 and 19.
  • the work connections AI and A2 which can be connected to work lines
  • Hydraulic pumps 10 and 11 The control line 20 of the first hydraulic pump 10 is connected to the
  • the control line 21 of the second hydraulic pump 11 is connected to the input X of the servo control unit 23 of the second hydraulic pump and to the input P2 of the servo control unit 22 of the first hydraulic pump 10.
  • the control pressure prevailing in the control line 20 is compared in a control valve 25 designed as a pressure compensator with the delivery pressure prevailing in the delivery pressure line 16.
  • the control valve is connected to the delivery pressure line 16 via a connecting line 24.
  • a pressure limiting valve 26 is connected downstream of the control valve 25 in order to limit the pressure in the control pressure line 27.
  • a servo control unit 23 of the second hydraulic pump 11 is provided with a control valve 28 which in any case works as a pressure compensator and which compares the pressure in the control line 21 with the delivery pressure in the delivery pressure line 17.
  • the control valve 28 is connected to the delivery pressure line 17 of the second hydraulic pump 11 via a connecting line 29.
  • a pressure limiting valve 30 is also connected downstream of the control valve 28 in order to limit the pressure in the signal pressure line 50.
  • the first hydraulic pump 10 is pivoted out by a swiveling device 31 in the direction of maximum delivery rate, while the second hydraulic pump 11 is also swung out in the direction of maximum delivery rate by a swiveling device 32.
  • the swivel-out device 31 or 32 consists of a piston 35 or 36 which can be acted upon against a spring 33 or 34.
  • the swivel-out device 31 or 32 acts on a pump actuator 37 or 38 which adjusts the delivery rate of the hydraulic pump 10 or 11.
  • A serves to reset the pump actuator 37 or 38 in the direction of a delivery rate reduction Pistons 39 and 40 which can be acted upon hydraulically.
  • the pistons 39 and 40 are acted upon by the signal pressure prevailing in the signal pressure line 27 or 50.
  • the control pressure in the control pressure line 25 or 28 which acts as a pressure compensator, increases the control pressure in the control pressure line 27 or 50 and thus the hydraulic pump 10 or 11 pivoted back in the direction of a reduction in the delivery rate until an equilibrium position is reached.
  • the control line 20 and 21 is connected to the pressure fluid tank 41 via a torque valve 42 and 43, respectively.
  • the valve piston 44 or 45 of the torque valve 42 or 43 is on the one hand from the control pressure in the control line 20 or 21 of the respectively assigned hydraulic pump 10 or 11 and on the other hand from the control pressure in the control line 21 or 20 of the other hydraulic pump 11 or 10 acted upon in the opening direction.
  • a measuring spring arrangement 46 or 47 acts on the valve piston 44 or 45, which in the exemplary embodiment consists of two individual springs in order to generate the linear characteristic curve, which was already explained with reference to FIG. 2.
  • the preload of the measuring spring arrangement 46 or 47 is determined by the position of the pump actuator 37 or 38.
  • control pressure in the control line 20 or the control pressure in the control line 21 reaches the value set on the torque valve 42 or 43, the torque valve 42 or 43 begins to open and there is a pressure drop on the throttle element 18 or 19.
  • the control valve 25 or 28 is opened further and supplies the piston 39 or 40 with an increased signal pressure, so that the latter strives to adjust the pump actuator 37 or 38 in the direction of a reduced delivery rate.
  • the measuring spring of the measuring spring arrangement 46 or 47 of the torque valve 42 or 43 is biased. In this way, constant power control is achieved.
  • valve sleeve 48 or 49 is also of the type in the control line 21 or 20 of the respective other hydraulic pump 11 or 10 prevailing control pressure. This further development according to the invention results in an improved approximation of the control characteristic of the power or torque control device to the ideally hyperbolic profile. This is described in more detail below with reference to FIG. 3.
  • Fig. 3 shows in a similar way as Fig. 2, the 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.
  • the first hydraulic pump 10 is adjusted to an approximately constant output on the real characteristic curve 1 ′ approximated to the ideal characteristic curve 1. If the second hydraulic pump 11 has an appreciable power output, the power output by the first hydraulic pump 10 must be reduced so that the total power output by the hydraulic pumps 10 and 11 does not exceed a predetermined maximum value and a drive unit driving the hydraulic pumps 10 and 11 is not overloaded.
  • FIG. 2 shows the control characteristic of a generic power or torque control device
  • FIG. 3 shows the characteristic, shown in FIG. 3, of the power or torque control device further developed according to the invention
  • the development according to the invention leads to an improved approximation of the control curve 2 " to the ideal rule series 2.
  • FIGS. 4 and 5 show a vertical longitudinal section through the moment valve 42
  • FIG. 5 shows a horizontal longitudinal section through the moment valve 42.
  • the torque valves 42 and 43 are formed in the same way, so that the following description is limited to the torque valve 42.
  • the torque valve 42 comprises a valve housing 60, a valve sleeve 61 which is axially movable in the valve housing 60 and a valve piston 62 which is movable with respect to the valve sleeve 61.
  • the valve piston 62 is acted upon by a spring plate 63 by the measuring spring arrangement 46 in the closing direction.
  • the measuring spring arrangement 46 consists of two individual springs 64 and 65 arranged one inside the other, which leads to the sectionally linear control characteristic which is shown in FIG. 3.
  • the preload of the spring assembly 46 is adjustable by means of a spring bolt 66.
  • a first pressure medium connection P1 is provided for the control line 20 and a second pressure medium connection P2 is provided in the valve housing 60 for the control line 21.
  • the pressure medium connection Pl connected to the control line 20 is connected to a first pressure chamber 67 via a connecting channel 75.
  • a first measuring surface 68 is acted upon by the control pressure prevailing in the control line 20 in the opening direction of the torque valve 42.
  • the torque valve 46 opens the control line 20 to the pressurized fluid tank 41.
  • the stepped bore 71 is connected to the transverse bore 73 via a connecting channel 72, so that the pressure fluid can flow into the leakage space 74.
  • the control line 21 connected to the pressure medium connection P2 is connected via a connecting channel 76 and via further connecting channels 77 and 78 to a second pressure chamber 79, on which a second measuring surface 80 is formed.
  • the control pressure prevailing in the control line 21 therefore also acts on the valve piston 72 in the opening direction of the torque valve 42.
  • control pressure prevailing in the control line 21 acts not only on the valve piston 62 but also also on the valve sleeve 61 in order to press it against one in dependence on the control pressure prevailing in the control line 21
  • a third Pressure chamber 82 is connected to the second pressure medium connection P2 via a connecting channel 90 which is only partially shown.
  • the control pressure of the second control line 21 prevailing in the pressure chamber 82 thus acts on a valve sleeve actuating piston 83.
  • the direction of movement of the valve sleeve actuating piston 83 is oriented perpendicular to the direction of movement of the valve sleeve 61. This leads to a particularly compact structure of the torque valve 42 according to the invention.
  • the valve sleeve actuating piston 83 acts on an intermediate member 84 which has a plate-like end 85 on the end face.
  • the intermediate member 84 has an inclined surface 86 which engages on a bolt element 87 formed on the valve sleeve 61. With a suitable, flat angle of inclination of the inclined surface 87, a reduction between the movement of the valve sleeve adjusting piston 83 and the movement of the valve sleeve 61 can be achieved, if necessary.
  • the intermediate member 84 is arranged within a driving pin 88 which is designed as a hollow cylinder and 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 lies flush against the inclined surface 86 of the intermediate member 84.
  • valve sleeve actuating piston 83 is biased at its end opposite the driving pin 88 by an actuating spring 100 so that the valve sleeve actuating piston 83 is pressed upward in FIG. 4 without being acted upon by the control pressure prevailing in the control line 21. In this way, the valve sleeve actuating piston 83 is reset.
  • the preload of the actuating spring 100 can be adjusted by adjusting the spring plate 101.
  • the adjustment of the spring plate 101 after removal of a housing sleeve 102 is accessible from the outside.
  • the pump actuator 3 By a horizontal displacement of the driving pin 88, the pump actuator 3 also acts on the valve sleeve 61.
  • the plate-like closure 85 of the intermediate element 84 ensures that the valve sleeve actuating piston 83 is in constant engagement with the intermediate element 84 despite the horizontal movement of the driving pin 88 in FIG. 4. Due to the vertical orientation in Fig. 4 Direction of movement of the valve sleeve actuating piston 83 perpendicular to the direction of movement of the valve sleeve 61 and the driving pin 88, the displacement of the valve sleeve 61 by the driving pin 88 on the one hand and by the valve sleeve adjusting piston 83 on the other hand can take place independently of one another.
  • the invention is not limited to the illustrated embodiment.
  • the torque valve can be designed in a variety of other ways.
  • the torque valve can have additional measuring surfaces for the control lines of the power or.
  • a separate pressure chamber must then be provided for each additional hydraulic pump to be connected to the valve sleeve actuating piston 83 for each additional hydraulic pump that can be connected, or a correspondingly large number of valve sleeve actuating pistons 83 are to be arranged in parallel.

Landscapes

  • 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.
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 true EP0954703A1 (fr) 1999-11-10
EP0954703B1 EP0954703B1 (fr) 2002-02-20

Family

ID=26030887

Family Applications (1)

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
US5562424A (en) 1995-09-12 1996-10-08 Caterpillar Inc. Pump displacement control for a variable displacement pump
US5567123A (en) * 1995-09-12 1996-10-22 Caterpillar Inc. Pump displacement control for a variable displacement pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9819069A1 *

Also Published As

Publication number Publication date
JP2001502771A (ja) 2001-02-27
WO1998019069A1 (fr) 1998-05-07
EP0954703B1 (fr) 2002-02-20
JP4082523B2 (ja) 2008-04-30
US6324841B1 (en) 2001-12-04

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