EP0149787B2 - Fördermengen-Regeleinrichtung für eine verstellbare Hydropumpe - Google Patents

Fördermengen-Regeleinrichtung für eine verstellbare Hydropumpe Download PDF

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Publication number
EP0149787B2
EP0149787B2 EP84115198A EP84115198A EP0149787B2 EP 0149787 B2 EP0149787 B2 EP 0149787B2 EP 84115198 A EP84115198 A EP 84115198A EP 84115198 A EP84115198 A EP 84115198A EP 0149787 B2 EP0149787 B2 EP 0149787B2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control
torque
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
EP84115198A
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German (de)
English (en)
French (fr)
Other versions
EP0149787A3 (en
EP0149787B1 (de
EP0149787A2 (de
Inventor
Gerhard Beutler
Heinz Berthold
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
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Filing date
Publication date
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Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
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Publication of EP0149787A3 publication Critical patent/EP0149787A3/de
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Publication of EP0149787B1 publication Critical patent/EP0149787B1/de
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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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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 flow control device according to the preamble of claim 1.
  • the torque valve is followed by the control valve, which acts as a pressure compensator and primarily serves to adjust the delivery rate.
  • the control valve acts as a pressure compensator and primarily serves to adjust the delivery rate.
  • DE-A 20 38 968 discloses a power control device for two or more hydraulic pumps and, moreover, the torque valve is not arranged in such a way that it connects the operating pressure control line depending on the pressure in the operating pressure control line and the preload of the measuring spring set with the unpressurized outlet.
  • a torque valve is known per se from FR-A 1,318,661, the spring of which is connected to the pump frame, but this known embodiment relates to a manually adjustable pump and, moreover, the torque valve is not controlled as a function of the pressure in the operating pressure control line.
  • the design and arrangement of the torque valve according to the invention in a flow control means that the torque valve can be attached to the hydraulic pump as a separate assembly and a driver pin of the pump actuator acts directly on the torque valve to change the preload of the measuring spring / measuring spring set depending on the flow rate setting. Since the torque characteristic is determined solely by the design of the characteristic of the measuring spring or the measuring spring set and the measuring spring is set directly via the driver pin, the preload of the measuring spring or the measuring spring set can be adjusted from outside by a stop in the torque valve by means of a handle.
  • any number of different torque characteristics can be preselected and also set or adjusted during operation, which is particularly advantageous when the pump torque is optimally adapted to the torque of the drive machine driving the pump.
  • a quick adaptation to any application is possible and such a moment valve can be used for pumps of different sizes and capacities without additional adaptation measures being necessary.
  • the stop in the torque valve can expediently be arranged on the end of the valve housing and be detachable for the exchange of the measuring spring / measuring spring set.
  • the torque control means is also suitable as total control for two or more drive side mechanically coupled hydraulic pumps, if according to the invention that the closing member of the momen - tenventils each pump from the sum of the pressure is applied in the operating pressure control line of the individual pump and the pressure in the operating pressure line of the other pump (s) and that each torque valve connects the operating pressure control line of its pump depending on the total operating pressure and the preload of its measuring spring with the unpressurized outlet.
  • the closing elements of the torque valves have several measuring surfaces which act in parallel and are each acted upon by the operating pressure of one of the pumps.
  • the hydraulic pump 1 is driven via the shaft 2 by a drive, not shown.
  • the pump actuator consists of a swivel element 3, the swivel angle a of which is proportional to the stroke volume of the hydraulic pump 1.
  • the servo actuator, not shown, for adjusting the swivel angle a comprises a spring 4 and a pressurizable actuating piston 5, the spring 4 adjusting the hydraulic pump 1 in the direction of the maximum swivel angle a, that is to say the maximum delivery volume.
  • An actuating piston 6 of the actuating device which can also be functionally combined with the piston 5, takes over the back part function in the direction of a smaller pivot angle a.
  • the control pressure acting on the piston 6 in the line 7 is removed via a control valve 8 and the line 9 from the delivery pressure line 10 of the hydraulic pump 1.
  • a common pressure relief valve 11 is located in series with the control valve 8.
  • the control valve 8 is designed as a pressure compensator and is acted upon on the one hand by the delivery pressure and on the other hand by a control pressure in the operating pressure control line 12, which controls the operating pressure of the hydraulic pump 1 behind a throttle 13 which limits the control flow operating pressure line 14 decreases after an optionally adjustable flow restrictor 15.
  • a moment valve 16 is acted upon on the one hand by the pressure in the control line 12 and on the other hand by a measuring spring or measuring spring set 17, the pretension of which is determined by the position of the piston 6 or the pump actuator 3.
  • the torque valve 16 can connect the control line 12 to the unpressurized outlet 18.
  • the operating pressure in the control line 12 reaches the value set on the torque valve 16 so that it begins to open, a pressure drop occurs at the control slide of the control valve 8 via the throttle 13.
  • the control slide is moved into the switching position 11 and supplies the piston 6 with Control pressure, so that it strives to adjust the actuator 3 of the hydraulic pump 1 in the direction of smaller flow rates.
  • the measuring spring 17 or the measuring spring set of the torque valve 16 is biased.
  • the measuring springs or the measuring spring set are designed in their spring characteristics. that, depending on the preload, an envelope is created in the theoretically desired power hyperbola.
  • a defined swivel angle a corresponds to a defined operating pressure in line 10.
  • the delivery rate setting of the hydraulic pump 1 in the area in which the torque control, that is to say the torque valve 16 has not yet responded is carried out in the usual way via the delivery rate throttle 15 and requires no special explanation.
  • FIG. 2 shows an embodiment of a torque valve 16 in its assignment to the pivotable pump actuator of an inclined-axis axial piston pump.
  • the pivotable actuator has a driver pin 20 projecting into the torque valve 16.
  • the torque valve 16 is designed as a seat valve arranged in a valve housing 21 with a valve cone 22 as a closing element, which is acted upon by a measuring spring set 17 formed from the springs 23 and 24.
  • the valve seat for the valve cone 22 is formed on a valve body 25 which is displaceably arranged in the valve housing 21 and on which the driver pin 20 of the pump actuator acts.
  • the valve body is acted upon by a spring 26 which is supported in the valve housing 21 and holds the valve body 25 in positive engagement with the driver pin 20.
  • the spring 23 of the measuring spring set 17 is supported on a stop 27 and the spring 24 on an adjusting screw .28 in the stop 27.
  • the stop 27 is screwed into the end of the valve housing 21. Due to the rotational position of the stop 27, the preload of the measuring spring set 17 and thus the position of the desired torque characteristics and the response point of the torque valve 16 can be adjusted.
  • the stop 27 has a handle 29. The course of the torque characteristics or the spring characteristic can be done by changing the preload of the spring 24 with the help of the adjusting screw 28.
  • the pressure present in the operating pressure control line 12 acts through the channel 30 in the valve body25 on the closing member 22 against the force of the measuring spring set 17.
  • the width of the valve seat determines the effective measuring area on the closing member 22 for the pressure in line 12. If the force exerted on the measuring surface by the pressure in line 12 exceeds the prestressing force of the measuring spring set 17, the valve cone of the closing member 22 lifts off the valve seat in the valve body 25 and opens the control line 12 to the unpressurized outlet, formed by the interior 31 of the valve housing 21 which is fixedly connected to the hydraulic pump, the interior 31 being connected to the unpressurized interior 32 of the hydraulic pump stands.
  • the driving pin 20 moves the valve body 25 in FIG. 2 to the right against the closing member 22 and thus increases the preload of the spring set 17 in accordance with the desired course of the torque characteristic.
  • the control device according to the invention is shown as a total torque control for two hydraulic pumps 33, 34, the drive shafts of which are driven directly or via a corresponding transfer gear 35 (only indicated schematically by a dash) by a common drive machine, not shown.
  • the control devices for the individual pumps correspond to the control device shown in FIG.
  • the same parts are provided with the same reference numerals and are not explained again.
  • Only the torque valves denoted by 16 in FIG. 1 are designed here as total torque valves 36 and differ from the torque valve 16 in that the closing element 22 according to FIG. 4 has an additional measuring surface 37.
  • the operating pressure of the other pump acts on this measuring surface 37 via a control line 38, 39.
  • the response that is to say the opening of the momentary valves 36 for the control pressure medium in the lines 12 for the unpressurized discharge, is thus dependent on the sum of the operating pressures.
  • Such regulations are necessary, for example, if two hydraulic pumps are driven by a common drive shaft or via a transfer case and the sum of the two torques of the pumps must not exceed the drive torque.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
EP84115198A 1983-12-14 1984-12-12 Fördermengen-Regeleinrichtung für eine verstellbare Hydropumpe Expired - Lifetime EP0149787B2 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE8335902U DE8335902U1 (ko) 1983-12-14 1983-12-14
DE3345264 1983-12-14
DE19833345264 DE3345264A1 (de) 1983-12-14 1983-12-14 Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe

Publications (4)

Publication Number Publication Date
EP0149787A2 EP0149787A2 (de) 1985-07-31
EP0149787A3 EP0149787A3 (en) 1985-08-21
EP0149787B1 EP0149787B1 (de) 1987-05-06
EP0149787B2 true EP0149787B2 (de) 1991-10-02

Family

ID=25816438

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84115198A Expired - Lifetime EP0149787B2 (de) 1983-12-14 1984-12-12 Fördermengen-Regeleinrichtung für eine verstellbare Hydropumpe

Country Status (4)

Country Link
US (1) US4668171A (ko)
EP (1) EP0149787B2 (ko)
JP (1) JPS60147588A (ko)
DE (2) DE8335902U1 (ko)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19646687C1 (de) * 1996-10-31 1998-02-12 Brueninghaus Hydromatik Gmbh Leistungs- bzw. Momentenregeleinrichtung für mehrere Hydropumpen
DE10001826C1 (de) * 2000-01-18 2001-09-20 Brueninghaus Hydromatik Gmbh Vorrichtung zum Regeln der Leistung einer verstellbaren Kolbenmaschine
US6324841B1 (en) 1996-10-31 2001-12-04 Brueninghaus Hydromatik Gmbh Power- and moment-regulating system for a plurality of hydraulic pumps

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3644769A1 (de) * 1986-12-30 1988-07-14 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer eine verstellbare hydrostatische maschine
DE3711050A1 (de) * 1987-04-02 1988-10-20 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen
DE3742111A1 (de) * 1987-04-02 1989-06-29 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen veraenderlichen foerder- bzw. schluckvolumens
DE3711053A1 (de) * 1987-04-02 1988-10-20 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen
JP2578371B2 (ja) * 1989-09-22 1997-02-05 株式会社小松製作所 可変容量ポンプの容量制御装置
DE4020325C2 (de) * 1990-06-26 1995-01-05 Hydrokraft Gmbh Regeleinrichtung für verstellbare Hydropumpen
DE4118869C2 (de) * 1991-06-07 1995-06-29 Hydromatik Gmbh Regelvorrichtung zur Regelung des Verdrängungsvolumens mehrerer hydrostatischer Maschinen
DE4141108A1 (de) * 1991-12-13 1993-06-17 Putzmeister Maschf Einrichtung zur regelung des ausgangsdruckes einer verstellpumpe
DE4202631C2 (de) * 1992-01-30 1995-07-06 Hydromatik Gmbh Axialkolbenmaschine, insbesondere Hydropumpe der Schiefscheibenbauart oder der Schrägachsenbauart, deren Durchsatzvolumen durch eine Einstellvorrichtung einstellbar ist
DE4208925C1 (ko) * 1992-03-19 1993-06-03 Hydromatik Gmbh, 7915 Elchingen, De
US5538401A (en) * 1994-07-05 1996-07-23 Denison Hydraulics Inc. Axial piston pump
KR100212645B1 (ko) * 1994-09-30 1999-08-02 토니헬샴 유압펌프의 토출유량 제어장치
DE19517974A1 (de) * 1995-05-16 1996-11-21 Brueninghaus Hydromatik Gmbh Verschiebbare hydraulische Leistungs- bzw. Momentenregeleinrichtung
JPH0986805A (ja) * 1995-09-25 1997-03-31 Kandenko Co Ltd ケーブルドラムの制動装置
DE19742157C2 (de) 1997-09-24 1999-07-01 Brueninghaus Hydromatik Gmbh Regeleinrichtung für eine verstellbare Hydropumpe mit mehreren Verbrauchern
DE19831587C2 (de) * 1998-07-14 2000-06-15 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung zur Regelung der hydraulischen Leistung einer Hydropumpe
DE10341331B3 (de) * 2003-09-08 2005-05-25 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung
EP2049800B1 (de) * 2006-08-21 2011-12-28 Joma-Polytec GmbH Förderpumpe
US8647075B2 (en) * 2009-03-18 2014-02-11 Eaton Corporation Control valve for a variable displacement pump
US9086143B2 (en) 2010-11-23 2015-07-21 Caterpillar Inc. Hydraulic fan circuit having energy recovery
DE102016123160A1 (de) * 2016-11-30 2018-05-30 Schwing Gmbh Großmanipulator mit schnell ein- und ausfaltbarem Knickmast
DE102017213458A1 (de) 2017-08-03 2019-02-07 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit Leistungsbegrenzung

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FR1318661A (fr) * 1961-12-27 1963-02-22 Sciper Sa Dispositif de sécurité pour pompes volumétriques
GB1126873A (en) * 1964-09-22 1968-09-11 Sperry Rand Corp Improvements in hydraulic supply and control systems
NL165340C (nl) * 1968-05-09 1981-03-16 Philips Nv Inrichting voor het opwekken van gestimuleerde infraroodemissie met een golflengte van ongeveer 10,6 mu bevattende middelen voor het instand houden van een elektrische ontlading in een gedeeltelijk uit kool- zuurgas bestaand gasmensel.
DE1921298B2 (de) * 1969-04-25 1973-08-23 Hydromatik Gmbh, 7900 Ulm Einrichtung zur regelung der foerdermenge verstellbarer axialkolbenpumpen
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19646687C1 (de) * 1996-10-31 1998-02-12 Brueninghaus Hydromatik Gmbh Leistungs- bzw. Momentenregeleinrichtung für mehrere Hydropumpen
US6324841B1 (en) 1996-10-31 2001-12-04 Brueninghaus Hydromatik Gmbh Power- and moment-regulating system for a plurality of hydraulic pumps
DE10001826C1 (de) * 2000-01-18 2001-09-20 Brueninghaus Hydromatik Gmbh Vorrichtung zum Regeln der Leistung einer verstellbaren Kolbenmaschine

Also Published As

Publication number Publication date
US4668171A (en) 1987-05-26
EP0149787A3 (en) 1985-08-21
EP0149787B1 (de) 1987-05-06
DE8335902U1 (ko) 1987-06-04
JPH0526955B2 (ko) 1993-04-19
DE3345264A1 (de) 1985-06-27
EP0149787A2 (de) 1985-07-31
JPS60147588A (ja) 1985-08-03

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