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EP0471166B1 - Dispositif de contrôle pour le réglage de l'ajustement du débit de plusieurs pompes hydrostatiques réglables - Google Patents

Dispositif de contrôle pour le réglage de l'ajustement du débit de plusieurs pompes hydrostatiques réglables Download PDF

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Publication number
EP0471166B1
EP0471166B1 EP91109890A EP91109890A EP0471166B1 EP 0471166 B1 EP0471166 B1 EP 0471166B1 EP 91109890 A EP91109890 A EP 91109890A EP 91109890 A EP91109890 A EP 91109890A EP 0471166 B1 EP0471166 B1 EP 0471166B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
line
valve
pump
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
EP91109890A
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German (de)
English (en)
Other versions
EP0471166A1 (fr
Inventor
Clemens Krebs
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 Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik 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 Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0471166A1 publication Critical patent/EP0471166A1/fr
Application granted granted Critical
Publication of EP0471166B1 publication Critical patent/EP0471166B1/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
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a control device according to the preamble of claim 1 for controlling the delivery volume setting of several hydrostatic pumps connected in parallel to a common consumer.
  • a control device each comprising a measuring and control unit assigned to the individual pumps with a pressure relief valve, a displacement transducer and a line provided with a throttle point.
  • the latter connects the inlet of the pressure relief valve with a line connected to the working pressure line of the respective pump and leads to a spring chamber of the pilot valve designed as a 3/2-way valve.
  • a spring in the spring chamber creates the counter pressure, which is opposed by the working pressure prevailing in the working pressure lines and in the consumer line.
  • the displacement sensor consists of an inclined surface formed on the piston rod of the adjusting piston of the adjusting cylinder and a tracer pin which is held in contact with the inclined surface by a spring, via which it acts on the slide of the pressure relief valve.
  • the pressure relief valve is closed to generate a correspondingly high pressure in the spring chamber when the assigned pump is set to zero delivery volume. It responds with increasing swiveling out of the pump in accordance with the movement of the inclined surface while reducing this pressure in the spring chamber.
  • the pressure difference at the pilot valve resulting from the pressure in the spring chamber and the counteracting working pressure represents the control pressure.
  • the delivery flows actually delivered by the individual pumps can be different, specifically because of interferences, such as different pump speeds, different structural tolerances, different friction and self-adjusting forces, and also different adjustment characteristics of the adjustment devices, etc.
  • Another disadvantage of the known control device is also the high design effort for the measuring and control units to generate the pressure in the spring chamber of the pilot valve.
  • each variable pump (swivel angle in the case of axial piston pumps) according to the invention
  • the delivery flow actually conveyed by each variable pump is detected by means of the respectively associated throttle, the pressure loss of which is functionally combined with the system pressure behind the throttle to the control pressure.
  • This control pressure acts on the pilot valve assigned to the respective variable displacement pump in the direction of the control position.
  • control pressure is therefore representative of the pressure difference present at the respective throttle, a measure of the delivery flow actually conveyed by the associated variable displacement pump, so that the regulation constructed as a pressure regulation is functionally a delivery flow regulation.
  • the back pressure can be in the form of a spring pressure and / or a hydraulic back pressure and can be adjustable if necessary.
  • a remote control valve for controlling the hydraulic back pressure is provided, which is common to all pilot valves. In this way it is possible to apply the same back pressure to all pilot valves in order to achieve the highest accuracy of the correction of the delivery volume setting in order to achieve the same delivery rates.
  • the remote control valve is designed as a pressure limiting valve, which is connected to a counterpressure control space and via a throttle point to the control pressure line of each pilot valve.
  • a pressure limiting valve which is connected to a counterpressure control space and via a throttle point to the control pressure line of each pilot valve.
  • the remote control valve can achieve the same Advantages can also be designed as a throttle element arranged in the consumer line, preferably in the form of a variable throttle valve, behind which a branch line leads to the counterpressure control chamber of each pilot valve.
  • the control device according to the invention is not only functionally but also structurally regulated flow rate.
  • Fig. 1 shows two or more hydrostatic variable pumps 1, 2 with a flow direction, which are connected in parallel via a working pressure line 3, 4 and a suction line 5, 6 to a common consumer line 7 or to the tank 10.
  • the consumer line 7 leads to at least one consumer (not shown).
  • Both variable pumps 1, 2 are each via a drive shaft 8, 9 by a common or each driven by a drive motor (not shown) and drain their leak oil via a leak oil line 11, 12 connected to the tank 10.
  • the suction lines 5, 6 can be connected to a common return line leading to the consumer instead of being connected to the tank 10.
  • the adjusting pumps 1, 2 are each assigned an adjusting device in the form of a hydraulic adjusting cylinder 13, 14 for adjusting their delivery volumes.
  • an adjusting piston 15 is slidably arranged and connected via a piston rod 16 to the adjusting part 17 of the respective adjusting pump 1, 2.
  • the adjusting piston 15 delimits a left cylinder chamber 18 with its (smaller) piston ring surface and a right cylinder chamber 19 with its (larger) piston surface.
  • An adjustable stop 20 for limiting the stroke of the adjusting piston 15 is arranged in each cylinder chamber 18, 19.
  • a compression spring 21 in the left cylinder chamber 18 acts on the adjusting piston 15 in the sense of a reduction in the size of the right cylinder chamber 19 and thus in the sense of a pivoting out of the variable pump 1, 2 to a larger delivery volume.
  • the cylinder spaces 18, 19 can be pressurized via a connection.
  • each adjusting cylinder 13, 14 takes place via a pilot valve 22, 23 in the form of a continuously adjustable 3/2-way slide valve with a connection to a first actuating pressure branch line 24 and to a second actuating pressure branch line 25.
  • the latter line leads to the right cylinder chamber 19 of the associated adjusting cylinder 13 or 14 and is also connected via a connecting line 27 having a throttle section 26 to a tank connection line 28 leading from the pilot valve 22 or 23 to the tank 10.
  • the first signal pressure branch line 24 leads to a control pressure line 29, which branches off at a branch 30 from the associated working pressure line 3 or 4. Via this control pressure line 29, the slide of the pilot valve 22 or 23 is acted upon in the direction of the control position against the counter pressure p G of a spring 31 arranged in a spring chamber.
  • a control pressure line section 32 leads from the control pressure line 29 to the connection of the left cylinder chamber 18 of the associated adjusting cylinder 13 or 14.
  • Each pilot valve 22, 23 is structurally a directly regulated pressure regulator.
  • Each spring chamber is connected to the tank connection line for relief.
  • a constant throttle 33, 34 is arranged between the branch 30 and the consumer line 7, which together with the associated pilot valve 22 or 23 represents a pressure regulator unit.
  • the totality of all pressure regulator units forms the control device according to the invention with the following function:
  • variable displacement pumps 1, 2 driven by the drive motor generate delivery flows Qi, which flow through the working pressure lines 3, 4 into the consumer line 7 and combine there to form a total delivery flow Qges loaded with a system pressure P Qges .
  • a pump pressure p Qi which is higher than the pressure behind the throttle, ie compared to the system pressure P Qges , increases by the pressure loss ⁇ p at this throttle, which acts on the respective pilot valve 22 or 23 as control pressure via the assigned control pressure line 29.
  • a maximum pump pressure P Qi builds up at the output of each variable pump 1, 2, which is greater than the system pressure P Qges by the pressure difference ⁇ p generated by the respective constant throttle 33 or 34 and corresponds to the set counter pressure p G or setpoint of the controlled variable .
  • Both variable pumps 1, 2 are constantly adjusted to this setpoint of the pump pressure p Qi and thus the corresponding system pressure p Qges during operation .
  • the assigned characteristic curves are shown in the pQ diagram according to FIG. 4. While the pump pressure characteristic curve p Qi runs parallel to the x-axis, the system pressure characteristic curve p Qges is a straight line that increases as the delivery volume setting of the variable pumps 1, 2 decreases and the pressure difference ⁇ p at the constant restrictors 33, 34 decreases.
  • the ordinate difference between the two characteristic curves at each operating point represents the respective pressure difference .DELTA.p. It shows that the pump or control pressure p Qi prevailing in the respective control pressure line 29, when viewed mathematically, consists of two components, namely the system pressure P Qges and the Pressure difference ⁇ p is composed.
  • both variable pumps 1, 2 are set to the same delivery volume and ideally deliver the same delivery flow; they therefore follow the same characteristic curve p Qi or P Qges .
  • deviations from the ideal case that are almost unavoidable are corrected with the control device according to the invention in the following manner.
  • variable displacement pump with a larger flow rate and thus a larger pump pressure p Qi or a larger pressure difference ⁇ p1 is pivoted back in the direction of a smaller flow volume and the variable displacement pump with a lower flow rate and thus lower pump pressure p Qi or smaller pressure difference ⁇ p2 swung out in the direction of the maximum delivery volume until the delivery flows generated by both variable pumps 1, 2 and thus the resulting pump pressures p Qi or pressure differences ⁇ p are the same without changing the total delivery flow and the system pressure P Qges .
  • control device shown in FIG. 2 is provided with a remote-controlled pressure control (structural view), but is otherwise identical to the control device according to FIG. 1.
  • the remote-controlled pressure control comprises a remote control valve in the form of a pressure limiting valve 35, which via a remote control line 36 and a remote control branch line 37 branching from each to the spring chamber of each pilot valve 22 or 23 and via a further line 38 with a throttle point 39 to the same pilot valve 22 or 23 leading control pressure line 29 is connected.
  • variable pump 1 or 2 The one on the respective variable pump 1 or 2
  • the resulting pressure difference associated with the throttle point 39 moves the slide of the respectively assigned pilot valve 22 or 23 against the spring pressure to the right into the control position, the respective variable pump 1 or 2 being pivoted back in the manner already described until the force balance on the respective pilot valve 22 or 23 prevails.
  • the regulation of both variable pumps 1, 2 to the same delivery flow takes place in the same way as with the directly controlled pressure control according to FIG. 1, namely by means of the control pressure p Qi and the increasing system pressure characteristic curve with decreasing delivery volume setting.
  • control device shown in FIG. 3 is provided with a flow control (structural view), but is otherwise identical to the control device according to FIG. 1.
  • the flow control comprises a remote control valve in the form of a variable throttle valve 40 arranged in the consumer line 7 and a branch line 41 which branches behind the variable throttle valve 40 in the direction of flow and leads via branch lines 42 to the spring chamber of each pilot valve 22, 23.
  • each pilot valve 22, 23 is acted upon by the pump pressure P Qi prevailing in the associated control pressure line 29 in the direction of the control position and by the counter pressure P G as the sum of the spring pressure and the system pressure P Qges in the branch line 41 and the associated branch line 42 in the direction of the rest position .
  • the pressure loss generated on each pilot valve 22, 23 by the respectively assigned constant throttle 33 or 34 as a function of the delivery flow Qi of the associated variable pump 1 or 2 and by the variable throttle valve 40 as a function of the total delivery flow P Qges acts as a Pressure difference ⁇ p against the spring pressure.

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

Claims (8)

  1. Dispositif de régulation du réglage du volume de refoulement de plusieurs pompes hydrostatiques réglables (1, 2) qui sont raccordées en parallèle, chacune par une conduite de pression du travail (3, 4), à une conduite d'utilisateur (7) allant à au moins un utilisateur commun et avec un dispositif de réglage (13, 14) sollicité par une pression de réglage pour le réglage de son volume de refoulement, chacune avec une vanne pilote (22, 23) associée à chaque dispositif de réglage, qui est sollicitée d'une part par une pression de commande (PQi) correspondant à la pression dans la conduite de pression de travail (3, 4) de la pompe réglable (1, 2) respective en tenant compte du réglage du volume de refoulement de cette pompe, en direction d'une position de régulation, et d'autre part par une contre-pression (PG), dans lequel, dans la position de régulation, la sollicitation du dispositif de réglage par la pression de réglage a lieu dans le sens d'une diminution du volume de refoulement de la pompe réglable associée,
    caractérisé en ce que la pression de commande (PQi) est prélevée en amont d'un étranglement (33, 34) dans la conduite de pression de travail (3, 4) de la pompe réglable (1, 2) respective et sollicite, par l'intermédiaire d'une conduite de pression de commande (29), la vanne pilote (22 ou 23) associée, en direction de la position de régulation.
  2. Dispositif de régulation selon la revendication 1, caractérisé en ce que chaque étranglement est un étranglement constant (33, 34).
  3. Dispositif de régulation selon la revendication 1 ou 2, caractérisé en ce que la contre-pression (PG) est la pression d'un ressort (31) et/ou une contre-pression hydraulique sollicitant une chambre de commande à contre-pression de la vanne-pilote (22, 23) respective.
  4. Dispositif de régulation selon au moins une des révendications précédentes, caractérisé en ce que la contre-pression (PG) est réglable.
  5. Dispositif de régulation selon au moins une des revendications précédentes, caractérisé par une vanne (35, 40) de commande à distance, commune à toutes les vannes pilotes (22, 23),pour commander la contre-pression hydraulique.
  6. Dispositif de régulation selon la revendication 5, caractérisé en ce que la vanne de commande à distance est sous la forme d'une vanne (35) limitant la pression et est raccordée à la chambre de commande à contre-pression ainsi que, par l'intermédiaire d'un étranglement (39),à la conduite de pression de commande (29) de chaque vanne pilote (22,23).
  7. Dispositif de régulation selon la revendication 5 ou 6, caractérisé en ce que la vanne de commande à distance est sous la forme d'un élément à étranglement (40) disposé dans la conduite d'utilisateur (7), en aval duquel une conduite dérivée (41) va à la chambre de commande à contre-pression de chaque vanne pilote (22, 23).
  8. Dispositif de régulation selon la revendication 7, caractérisé en ce que l'élément à étranglement est une vanne à étranglement réglable (40).
EP91109890A 1990-08-13 1991-06-17 Dispositif de contrôle pour le réglage de l'ajustement du débit de plusieurs pompes hydrostatiques réglables Expired - Lifetime EP0471166B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4025638A DE4025638C1 (fr) 1990-08-13 1990-08-13
DE4025638 1990-08-13

Publications (2)

Publication Number Publication Date
EP0471166A1 EP0471166A1 (fr) 1992-02-19
EP0471166B1 true EP0471166B1 (fr) 1994-05-18

Family

ID=6412164

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91109890A Expired - Lifetime EP0471166B1 (fr) 1990-08-13 1991-06-17 Dispositif de contrôle pour le réglage de l'ajustement du débit de plusieurs pompes hydrostatiques réglables

Country Status (3)

Country Link
US (1) US5226289A (fr)
EP (1) EP0471166B1 (fr)
DE (2) DE4025638C1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4208925C1 (fr) * 1992-03-19 1993-06-03 Hydromatik Gmbh, 7915 Elchingen, De
DE4214770C1 (de) * 1992-05-04 1993-10-07 Brueninghaus Hydraulik Gmbh Regelvorrichtung zur Regelung des Verdrängungsvolumens einer hydrostatischen Maschine
JP3575827B2 (ja) * 1994-06-08 2004-10-13 東芝機械株式会社 可変容量ポンプのロードセンシング装置
US5937646A (en) * 1997-07-10 1999-08-17 Mi-Jack Products Hydraulic charge boost system for a gantry crane
US6109030A (en) * 1998-02-13 2000-08-29 Sauer Inc. Apparatus and method for ganging multiple open circuit pumps
US6932583B2 (en) * 2001-04-16 2005-08-23 Siemens Diesel Systems Technology Multiple stage pump with multiple external control valves
US20120070108A1 (en) * 2010-09-17 2012-03-22 Leonid Kashchenevsky Hydrostatic arrangement for a spin welding machine and method of supporting spindle for the same
DE102015000869B4 (de) * 2015-01-23 2019-10-24 Dürr Systems Ag Pumpenanordnung und entsprechendes Betriebsverfahren
DE102020211285A1 (de) * 2020-02-13 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulischer Lüfterantrieb

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US3856436A (en) * 1972-12-18 1974-12-24 Sperry Rand Corp Power transmission
GB1526085A (en) * 1975-11-04 1978-09-27 Plessey Co Ltd Hydraulic pumping arrangements
DE2906166A1 (de) * 1979-02-17 1980-08-28 Bosch Gmbh Robert Einrichtung zur regelung des foerderstroms und zur begrenzung des foerderdrucks einer verstellbaren pumpe
DE2913534A1 (de) * 1979-04-04 1980-10-16 Bosch Gmbh Robert Einrichtung zur regelung des foerderstroms und zur begrenzung des foerderdrucks einer verstellbaren pumpe
DE3044143A1 (de) * 1980-11-24 1982-06-24 Linde Ag, 6200 Wiesbaden Steuereinrichtung fuer ein hydrostatisches antriebssystem
EP0078861B1 (fr) * 1981-11-10 1985-03-20 Vickers Systems GmbH Système de réglage de pression
DE3513452A1 (de) * 1985-04-15 1986-10-16 Mannesmann Rexroth GmbH, 8770 Lohr Hydrauliksystem fuer die versorgung einer hydrostatischen lenkung
DE3711050A1 (de) * 1987-04-02 1988-10-20 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen
DE3711053A1 (de) * 1987-04-02 1988-10-20 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen
DE3711049A1 (de) * 1987-04-02 1988-11-10 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen
US4813235A (en) * 1987-06-09 1989-03-21 Deere & Company Hydraulic gain reduction circuit
EP0329860A1 (fr) * 1988-02-25 1989-08-30 RIVA CALZONI S.p.A. Dispositif d'alimentation et de commande de la vitesse et du couple d'un moteur hydraulique à cylindrée variable et pression constante

Also Published As

Publication number Publication date
DE4025638C1 (fr) 1991-12-05
US5226289A (en) 1993-07-13
EP0471166A1 (fr) 1992-02-19
DE59101655D1 (de) 1994-06-23

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