EP0471166A1 - 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
EP0471166A1
EP0471166A1 EP91109890A EP91109890A EP0471166A1 EP 0471166 A1 EP0471166 A1 EP 0471166A1 EP 91109890 A EP91109890 A EP 91109890A EP 91109890 A EP91109890 A EP 91109890A EP 0471166 A1 EP0471166 A1 EP 0471166A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
line
pump
throttle
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
EP91109890A
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German (de)
English (en)
Other versions
EP0471166B1 (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
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Publication date
Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0471166A1 publication Critical patent/EP0471166A1/fr
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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 to a control pressure 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 generates the counter pressure, which is opposed by the working pressure prevailing in the working pressure lines and in the consumer line as the first control pressure.
  • the displacement transducer 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 second control pressure when the assigned pump is set to zero delivery volume. As the pump swings out, it responds more in accordance with the movement of the inclined surface while reducing the second control pressure.
  • Another disadvantage of the known control device is also the high design effort for the measuring and control units for generating the second control pressure.
  • each variable pump in contrast to the prior art, instead of adjusting the delivery volume of each variable pump (swivel angle in the case of axial piston pumps), the delivery flow actually delivered by each variable pump is recorded according to the invention by means of the respectively associated throttle, the pressure loss of which is functionally related to the first control pressure, the system pressure behind the throttle, to the second Control pressure is combined.
  • This second control pressure acts as the only control pressure on the pilot valve assigned to the respective variable displacement pump in the direction of the control position.
  • the second control pressure is therefore representative of the pressure difference present at the respective throttle, a measure of the delivery flow actually delivered by the associated variable displacement pump, so that the control constructed as a pressure control is functionally a delivery flow control.
  • the chokes used in accordance with the invention to achieve these advantages have a constructional expenditure which is negligible compared to the measuring and control units used in the prior art.
  • the back pressure can be 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 in correcting 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.
  • 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.
  • the remote control valve 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 counter-pressure 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 driven via a drive shaft 8, 9 by a common or one drive motor (not shown) and discharge their leak oil via a leak oil line 11, 12 each connected to the tank 10.
  • the suction lines 5, 6 can be connected to a common return line leading to the consumer instead of the connection 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 to the adjusting part 17 of the respective adjusting pump 1, 2 via a piston rod 16.
  • 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-hand cylinder chamber 18 acts on the adjusting piston 15 in the sense of a reduction in the size of the right-hand cylinder chamber 19 and thus in the sense of a pivoting out of the adjusting 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 maximum pump pressure P Q builds up at the outlet of each variable pump 1, 2; which is greater than the system pressure P Qges by the pressure difference A p generated by the respective constant throttle 33 or 34 and corresponds to the set back pressure p G or setpoint of the controlled variable. Both variable pumps 1, 2 are continuously 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.
  • the system pressure characteristic curve p Qges is a straight line that increases the pump pressure characteristic curve as the delivery volume setting of the variable displacement pumps 1, 2 and thus the pressure difference A p at the constant restrictors 33, 34 decrease p Qi cuts at zero delivery volume.
  • the ordinate difference occurring at each operating point between the two characteristic curves represents the respective pressure difference A p.
  • the pump or second control pressure p Qi prevailing in the respective control pressure line 29 from a mathematical point of view consists of two components, namely the system pressure p Qges as first control pressure and the pressure difference A 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 pumps 1, 2 Different flow rates due to, for example, differing delivery volume settings of the variable pumps 1, 2 generate different pressure differences A p at the constant restrictors 33, 34. Since the system pressure P Qges (first control pressure) in the consumer line 7 is the same for both variable pumps 1, 2, different pump pressures p Qi arise at the outputs of both variable pumps 1, 2, which serve as second control pressures via the control pressure lines 29, the pilot valves 22, 23 act upon.
  • 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 relief valve 35, which via a remote control line 36 and a remote control branch line 37 branching off 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 shifts the slide of the respectively assigned pilot valve 22 or 23 to the right against the spring pressure into the control position, the respective variable pump 1 or 2 being pivoted back in the manner already described until force equilibrium prevails at the respective pilot valve 22 or 23.
  • 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 second 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 downstream of the variable throttle valve 40 and leads via branch lines 42 to the spring chamber of each pilot valve 22, 23.
  • each pilot valve 22, 23 is controlled by the pump pressure p Qi 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 PO g es in the branch line 41 and the associated branch line 42 in the rest position acted upon.
  • the pressure loss generated by the associated constant throttle 33 or 34 as a function of the delivery flow Qi of the associated adjusting pump 1 or 2 and from the variable throttle valve 40 as a function of the total delivery flow PO g it acts as a pressure difference on each pilot valve 22, 23 A 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)
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
DE4025638 1990-08-13
DE4025638A DE4025638C1 (fr) 1990-08-13 1990-08-13

Publications (2)

Publication Number Publication Date
EP0471166A1 true EP0471166A1 (fr) 1992-02-19
EP0471166B1 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
DE102020211288A1 (de) * 2020-02-13 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulisches Antriebssystem

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2211054A5 (fr) * 1972-12-18 1974-07-12 Sperry Rand Corp
GB2042219A (en) * 1979-02-17 1980-09-17 Bosch Gmbh Robert Apparatus for regulating the delivery flow and for limiting the delivery pressure from an adjustable pump
EP0078861A1 (fr) * 1981-11-10 1983-05-18 Vickers Systems GmbH Système de réglage de pression
EP0284988A2 (fr) * 1987-04-02 1988-10-05 BRUENINGHAUS HYDRAULIK GmbH Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1526085A (en) * 1975-11-04 1978-09-27 Plessey Co Ltd Hydraulic pumping arrangements
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
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
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

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2211054A5 (fr) * 1972-12-18 1974-07-12 Sperry Rand Corp
GB2042219A (en) * 1979-02-17 1980-09-17 Bosch Gmbh Robert Apparatus for regulating the delivery flow and for limiting the delivery pressure from an adjustable pump
EP0078861A1 (fr) * 1981-11-10 1983-05-18 Vickers Systems GmbH Système de réglage de pression
EP0284988A2 (fr) * 1987-04-02 1988-10-05 BRUENINGHAUS HYDRAULIK GmbH Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune

Also Published As

Publication number Publication date
EP0471166B1 (fr) 1994-05-18
DE4025638C1 (fr) 1991-12-05
DE59101655D1 (de) 1994-06-23
US5226289A (en) 1993-07-13

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