EP0423257B1 - Dispositif pour pompes hydrostatiques a refoulement variable - Google Patents

Dispositif pour pompes hydrostatiques a refoulement variable Download PDF

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Publication number
EP0423257B1
EP0423257B1 EP90903003A EP90903003A EP0423257B1 EP 0423257 B1 EP0423257 B1 EP 0423257B1 EP 90903003 A EP90903003 A EP 90903003A EP 90903003 A EP90903003 A EP 90903003A EP 0423257 B1 EP0423257 B1 EP 0423257B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
pump
delivery
control valve
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
EP90903003A
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German (de)
English (en)
Other versions
EP0423257A1 (fr
Inventor
Gerhard Nonnenmacher
Egon Tittmann
Heinz Walter
Walter Robeller
Dieter Bertsch
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0423257A1 publication Critical patent/EP0423257A1/fr
Application granted granted Critical
Publication of EP0423257B1 publication Critical patent/EP0423257B1/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 device on an adjustable hydrostatic pump for regulating the flow rate and possibly also the discharge pressure of the same.
  • the demands on the actuating speed of such adjustable pumps have grown considerably.
  • One of the limits for this positioning speed is the pressure level of the positioning current. This is generally taken from the pump's own flow rate, which is why its pressure can reach a maximum of the pump outlet pressure. If the pump's working pressure is low, this inevitably leads to restrictions in the actuating speed.
  • solutions are known - for example according to FIG. 1 of the drawing - which connect the control system to an auxiliary pressure source in phases of low working pressure. This can be an external pressure supply or a pressure storage system that is recharged from the own pump circuit during the high pressure phase in the work cycle.
  • an adjustable pump with a pressure control has become known, a 3-way valve with two switching positions being arranged between the pressure control device and the adjusting cylinder. In one switch position, the control pressure-controlled cylinder space of the adjusting cylinder is brought into operative connection with the pressure control device and in the other switching position, the other control pressure-controlled cylinder space of the adjustment cylinder is brought into connection with the tank.
  • the aim of this is to ensure that the adjustable hydraulic pump operates with a reduced delivery rate during the start-up period of the electric drive machine, so that overloading of the drive machine is reliably prevented regardless of the pressure setting of the pressure control device. With this known pump or device, however, the aim of the present invention is not achieved.
  • a power piston is connected to the control piston, the piston chamber facing away from the control piston being directly connected to the pressure line connected to the pressure accumulator and its piston chamber facing the control piston to the cylinder chamber of the actuating cylinder controlled by the control valve.
  • the device according to the invention with the characterizing features of the main claim has the advantage that the control piston is supplied in the different positions of the control valve from different control pressure sources. This way you get. both a high actuating speed and an extremely precise setting of the pump or the pressure medium flow that it pumps. Further advantages of the invention emerge from the subclaims and the following description and drawing.
  • FIG. 1 shows a schematic representation of a device for pressure and current control for an adjustable pump according to the prior art in FIG. 1, a first exemplary embodiment of the invention in FIG. 2, deviating from the above exemplary embodiment, and a modification of the inventive example according to FIG. 2 in FIG. 3 , in Figures 4 and 5 further modifications.
  • FIG. 1 which - as mentioned above - shows a device for regulating the delivery flow and - optionally - also the delivery pressure of an adjustable pump according to the prior art - 10 denotes an adjustable pump, the actuator 11 of which with the aid of two pressurized pumps , uneven area piston 12, 13 is set.
  • the pump 10 sucks pressure medium from a container 14 and displaces it into a delivery line 15 in which an adjustable measuring throttle 16 is arranged.
  • a line 17 is connected to the delivery line 15, which leads to the smaller-area control piston 13.
  • a line 19, which leads to an adjustable pilot valve 20 and in which a throttle 19 is arranged, is connected to the feed line 15 behind the measuring throttle 16.
  • a line 21 leads from line 19 to the right end face 22A of a 3/3 control valve 22 with the switching positions I to III with a smooth transition.
  • a regulator spring 23 also acts on the end face 22A.
  • a line 24 opens, which starts from a line 25 which is connected to the delivery line 15 and which via a first check valve 69 leads to a line 33, via a second check valve 70 to a line 36 and to a pressure accumulator 26 leads.
  • a line 27 continues from the delivery line 15, which opens into the line 36 via a check valve 28 and a throttle 35.
  • the pressure drop at this measuring throttle on the end faces 22A and 22B of the control valve 22 generates a force which corresponds to the force of the control spring 23 in the position II of the control valve.
  • a small current flows from the line 33, 30, which is at least under pump delivery pressure via the check valve 69, into the line 31.
  • An identical pressure medium flow from the line 31 to the tank 14 flows via line 34, control edge 67 and line 29 No current flows to the control piston 12 or back from there, the pump therefore maintains its current position.
  • the pressure difference at the measuring throttle 16 is smaller than that specified by the control spring 23, and the control valve is moved to position III. Thereupon the outflow from line 31 via control edge 67 to the tank is interrupted and instead a further connection to line 30 is opened, via which pressure medium flows to line 31. Now the pressure in the setting piston 12 rises and adjusts the pump to a larger delivery volume.
  • the control valve 22 becomes the pressure regulator.
  • the pilot valve (20) opens, the pressure in the line 21 drops suddenly, and the control valve 22 is switched to switch position I. Now the control piston 12 is connected to the container, while the control piston 13 resets the pump and lowers the delivery pressure. Without positions 20 and 18, the control valve 22 is a pure flow control.
  • the control valve must therefore correct the pressure divider ratio in the switching position II, which is decisive for the accuracy, with every fluctuation in the system pressure. This is done by a small change in the discharge cross-section at the control edge 67, that is to say by correcting the equilibrium position. As a result, the effective control pressure gradient fluctuates and the accuracy of the delivery flow deviates from the high standard that applies to identical control and working pressures.
  • a line 76 with a built-in throttle 72 is led from line 25 to a line 71 which starts from control valve 22 and leads to actuating piston 12 .
  • This is part of the line 31 according to the exemplary embodiment in FIG. 1, but is now omitted in its area from line 30 to line 34.
  • the high-pressure line 25 is now connected directly to the control line 71 to the control piston 12 via the throttle 72.
  • the actuating piston 12 is supplied in the different switching positions of the regulating valve 22 by different control pressure sources, that is, once directly from the pump delivery pressure via line 76, another time via line 30 from the pressure accumulator 26, provided that its pressure is higher than the pump pressure.
  • Position I The differential pressure force created by the pressure drop at the measuring throttle 16 or the throttle 18 is larger than the average force of the governor spring 23, that is, during the current controller is Q is greater than Q should, in the pressure regulator P is larger than P soll.
  • the control piston 12 is now connected to the container via the control valve. Due to the pressure acting on the actuating piston 13, the pump is adjusted in the direction of a smaller stroke volume.
  • control valve 22 In switch position II the control valve 22 is the differential pressure force is equal to the average force of the governor spring 23, that is, during the current controller Q is equal to Q should, in pressure regulation is P is equal to P.
  • a small flow of pressure medium flows from the high pressure side of the pump to the control piston 12 via the throttle 72.
  • pump position In the state of equilibrium of the control valve (pump position equals setpoint), an equally large flow of pressure medium flows from the control piston connection to the tank via the throttle control edge 67.
  • the current delivery position of the pump is therefore retained. Even small deviations from the setpoint briefly change the equilibrium position and the discharge cross-section. Such deviations thus lead to sensitive correction of the delivery volume in the usual way.
  • the choke 72 in line 76 which here as external Throttle is shown, can also within the control valve 22, for. B. be formed as a bevel on a control collar.
  • the pump controller according to the invention thus combines the high control accuracy of a conventional controller with the high actuating speed of a pump adjustment supplied with external pressure.
  • FIG. 3 shows a variant of the exemplary embodiment according to FIG. 2.
  • the storage line 36 is routed to a special connection of the control valve 22.
  • four different switching positions are drawn for the control valve 22 (any number of intermediate positions can be represented in the smooth transition between the positions).
  • the mode of operation corresponds to the exemplary embodiment according to FIG. 3.
  • the control valve behaves in the switching positions I-III like a conventional regulator (eg that according to FIG. 1 without the external pressure line 36). The usual accuracy of a current or pressure current regulator is therefore fully retained.
  • the invention can also be implemented in a design with two separate control valves for current and pressure control.
  • the current regulator is designated 80, the pressure regulator 81.
  • the connection from the pressure accumulator 26 leads through both valves and then has a connection to the actuating piston 12.
  • the differential pressure at the measuring throttle 16 at the pressure regulator 81 the absolute delivery pressure of the pump .
  • the direct connecting line from the high-pressure side of the pump to the pressure connection for the actuating piston 12 is designated 82, the throttle arranged in it is 83.
  • a compression spring can be used as a counterforce to the actuating piston 12 instead of the actuating piston 13.

Landscapes

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

Abstract

Un dispositif comprend un piston de réglage (12) de l'organe de réglage (11) de la pompe (10) à refoulement variable, commandé par une pression de commande. La pression de commande est générée par une soupape de réglage (22) qui reçoit la pression différentielle générée au niveau d'un étranglement de mesure (16) de la conduite de refoulement (15) de la pompe. En outre, un ressort de pression (23) agit sur la soupape de réglage contre la pression plus élevée. Une alimentation extérieure en pression (26) (accumulateur de pression) fournit la pression de commande. En outre, il existe une communication directe (70) à étranglement (72) entre le côté de haute pression et le raccord de la pression de commande du piston de réglage (12).

Claims (5)

  1. Dispositif sur une pompe hydrostatique réglable (10) pour la régulation du débit de refoulement et, éventuellement aussi, de la pression de refoulement de cette pompe, dispositif dont l'organe de réglage (11) est susceptible d'être positionné contre une force antagoniste à l'aide d'au moins un piston de réglage (12) sollicité par une pression de réglage ou bien susceptible d'être déchargé de celle-ci, tandis que la pression de réglage est formée dans un distributeur de réglage (22) et en fait, pour un équilibre approximatif de la valeur réelle et de la valeur de consigne du débit de refoulement ou bien de la pression de refoulement, par un diviseur de pression qui est constitué par la combinaison d'un étranglement fixe (32, 72) et d'un étranglement variable (67) dans le distributeur de réglage, sur lequel agit la différence de pression d'un étranglement de mesure (16) disposé sur la canalisation de roulement (15) ou bien la différence de pression d'un étranglement (18) disposé sur la canalisation (19) allant à une vanne pilote (20), ainsi que par un ressort régulateur (23) qui agit contre la plus élevée des deux pressions sur la distributeur de réglage (22), en outre, avec une source de pression auxiliaire (26) dont la pression peut agir indirectement ou directement par l'intermédiaire du distributeur de réglage sur le piston de réglage (12), dispositif caractérisé en ce que la pression de réglage, dans les limites d'une coïncidence approximative entre la valeur réelle et la valeur de consigne, est obtenue par l'intermédiaire du diviseur de pression (72, 67) à partir de la pression du débit de refoulement de la pompe (position de commutation (II), par contre, dans le cas d'un écart plus important, elle provient de la source de pression plus élevée pour modifier la position de la pompe (position de commutation III ou bien IV), et en ce que le piston de réglage (12) est déchargé vers le réservoir pour ramener la pompe à sa position initiale (position de commutation I).
  2. Dispositif selon la revendication 1, caractérisé en ce qu'une canalisation de liaison (76, 71), dans laquelle est disposé l'étranglement fixe (72), part de la canalisation de refoulement (15) vers le piston de réglage (12).
  3. Dispositif selon la revendication 1, caractérisé en ce que la liaison entre la canalisation de refoulement (25) et la canalisation de raccordement pour le piston de réglage est indirecte et passe par l'intermédiaire du distributeur de réglage (22).
  4. Dispositif selon la revendication 1, caractérisé en ce que la distributeur de réglage est constituée par deux vannes spatialement distinctes, à savoir un régulateur de débit (80) et un régulateur de pression (81).
  5. Dispositif selon une des revendications 1 à 4, caractérisé en ce que la source de pression auxiliaire (26) est un accumulateur de pression, qui pour une pression de fonctionnement élevée est chargé à partir de la canalisation de refoulement par l'intermédiaire d'une soupape de retenue (28) et d'un étranglement (35).
EP90903003A 1989-03-08 1990-02-16 Dispositif pour pompes hydrostatiques a refoulement variable Expired - Lifetime EP0423257B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3907409A DE3907409A1 (de) 1989-03-08 1989-03-08 Einrichtung an einer verstellbaren hydrostatischen pumpe
DE3907409 1989-03-08

Publications (2)

Publication Number Publication Date
EP0423257A1 EP0423257A1 (fr) 1991-04-24
EP0423257B1 true EP0423257B1 (fr) 1993-07-21

Family

ID=6375787

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90903003A Expired - Lifetime EP0423257B1 (fr) 1989-03-08 1990-02-16 Dispositif pour pompes hydrostatiques a refoulement variable

Country Status (4)

Country Link
US (1) US5173031A (fr)
EP (1) EP0423257B1 (fr)
DE (2) DE3907409A1 (fr)
WO (1) WO1990010793A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5133644A (en) * 1991-01-17 1992-07-28 Halliburton Company Multi-pressure compensation of variable displacement pump
DE4141108A1 (de) * 1991-12-13 1993-06-17 Putzmeister Maschf Einrichtung zur regelung des ausgangsdruckes einer verstellpumpe
US5344288A (en) * 1993-01-28 1994-09-06 Kabushiki Kaisha Komatsu Seisakusho Device for controlling displacement of variable displacement hydraulic pump
DE4420619A1 (de) * 1994-06-13 1995-12-14 Rexroth Mannesmann Gmbh Antriebssystem mit hydrostatischen Maschinen
US6179223B1 (en) * 1999-08-16 2001-01-30 Illinois Tool Works Spray nozzle fluid regulator and restrictor combination
DE19956553B4 (de) * 1999-11-24 2010-11-25 Robert Bosch Gmbh Verfahren zum Abschätzen des Druckes in einem Radbremszylinder und Steuereinheit zur Durchführung des Verfahrens
DE102017206415A1 (de) * 2017-04-13 2018-10-18 Danfoss Power Solutions Gmbh & Co. Ohg Selbsterhaltende stromversorgung für hydrostatische pumpen und motoren
DE102018212042A1 (de) * 2018-07-19 2020-01-23 Robert Bosch Gmbh Hydromaschine mit geregeltem Verdrängungsvolumen
WO2021127634A1 (fr) 2019-12-20 2021-06-24 Clark Equipment Company Commande à régulation externe pour pompe d'entraînement

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1922145A1 (de) * 1969-04-25 1970-10-29 Bellows Valvair Kaemper Gmbh Kombinationsregler
BE757640A (fr) * 1969-10-16 1971-04-16 Borg Warner Systemes hydrauliques, notamment pour la regulation d'une pompea debit variable
DE2206788A1 (de) * 1972-02-12 1973-08-23 Rexroth Gmbh G L Verstellbare hydropumpe mit druckregelung
DE2349124C2 (de) * 1973-09-29 1985-09-05 Mannesmann Rexroth GmbH, 8770 Lohr Steuervorrichtung für eine im Speicherbetrieb arbeitende hydraulische Verstellpumpe
DE2551088C2 (de) * 1975-11-14 1984-06-28 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zur Mengen- und Druckregelung für Verstellpumpen
DE2904474A1 (de) * 1979-02-07 1980-08-28 Bosch Gmbh Robert Stromregeleinrichtung fuer eine verstellbare 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
DE2952083A1 (de) * 1979-12-22 1981-06-25 Robert Bosch Gmbh, 7000 Stuttgart Regeleinrichtung fuer eine verstellbare pumpe

Also Published As

Publication number Publication date
US5173031A (en) 1992-12-22
DE59002027D1 (de) 1993-08-26
WO1990010793A1 (fr) 1990-09-20
EP0423257A1 (fr) 1991-04-24
DE3907409A1 (de) 1990-09-20

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