EP0093916A1 - Control apparatus for a variable displacement pump - Google Patents

Control apparatus for a variable displacement pump Download PDF

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Publication number
EP0093916A1
EP0093916A1 EP83103940A EP83103940A EP0093916A1 EP 0093916 A1 EP0093916 A1 EP 0093916A1 EP 83103940 A EP83103940 A EP 83103940A EP 83103940 A EP83103940 A EP 83103940A EP 0093916 A1 EP0093916 A1 EP 0093916A1
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EP
European Patent Office
Prior art keywords
pressure
lever
pump
control
force
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EP83103940A
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German (de)
French (fr)
Inventor
Gerhard Dipl.-Ing. Nonnenmacher
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, 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
    • F04B49/002Hydraulic systems to change the pump delivery
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, 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
    • F04B49/08Regulating by delivery pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00Pump parameters
    • F04B2201/12Parameters of driving or driven means
    • F04B2201/1203Power on the axis

Definitions

  • the invention relates to a control device according to the type of the main claim.
  • the stroke volume of the pump changes linearly with this pressure within a certain range of the control pressure.
  • the design can be done with a positive or negative gradient, i. H. the stroke volume increases or decreases with increasing control pressure.
  • Such a device has the disadvantage that the machine driving the pump can be overloaded.
  • the device according to the invention with the characterizing features of the main claim has the advantage that with it, depending on the working pressure Control pressure is formed so that the product of the stroke volume times the working pressure of the pump remains constant. For constant drive speed, this means constant power on the drive machine. This cannot be overloaded. It is essential that the device according to the invention generates an exact performance hyperbole and allows a simple change in the selected performance level.
  • control pressure does not have to be generated by an auxiliary pump, but can be obtained directly from the working pressure of the pump.
  • FIG. 1 shows a first exemplary embodiment in a schematic representation
  • FIG. 2 shows a diagram
  • FIG. 3 shows a second exemplary embodiment
  • FIG. 4 shows a second diagram
  • FIG. 5 shows a third exemplary embodiment again in a schematic representation.
  • 10 denotes an adjustable pump, the stroke ring 11 of which can be adjusted by means of a pressurized actuating piston 12 against a counterforce 13 for the purpose of changing the stroke of the pistons.
  • the control piston 12 receiving bore 14 opens a line 15 which comes from a valve 16.
  • the valve 16 is symbolically represented as a 3/3-way valve which has smooth or continuous transitions between the individual switching positions I-III. This is symbolically represented by the two parallel lines.
  • a line 18 branches off from line 15 and leads to the left end A of the valve spool. This is articulated on a lever 20 via a rod 19 or a plunger.
  • a line 23 leads to the valve 16 of this line 24 to a container 25 'between lines 23 and 24, a pressure limiting valve 26' is arranged.
  • the lever 20 is pivotable about a pivot point 25 '.
  • the position of the pivot point is predetermined by a roller 27 arranged on a piston rod 26.
  • the piston 28 connected to the piston rod 26 is guided in a cylinder 29 and is acted upon by the working pressure of the pump 10 against the force of a spring 31 via a line 30.
  • a control process looks like this: If, for example, the working pressure p rises at a certain stroke volume of the pump 10, the piston 28 is displaced against the force of the spring 31 and the lever arm b becomes larger. This means that the left-turning moment A times p st times b increases and outweighs the right-turning moment F 1 times a.
  • the lever 20 now pivots counterclockwise about the pivot point 25 ', as a result of which the valve 16 is moved from its neutral position II into the working position I. This allows pressure medium to flow out of the bore 14 to the container 25.
  • the spring 13 then adjusts the pump to a lower delivery rate, namely until the right-hand turning moment due to the decreasing pressure p st the lever 20 and thus that Brings valve 16 back to its previous position.
  • the valve 16 acts as a pressure reducing valve with a continuous transition between the blocking position and the working positions I and III.
  • the pressure Ph generated by the auxiliary pump 22 is converted by the valve into the pressure Pst - see the formulas above.
  • the pump 10 is set so that the product of the delivery volume and working pressure is always constant, i. H. these values form an exact hyperbola.
  • the force F 2 on the lever arm b which corresponds to p o , causes the pump to be released only at a certain pressure, e.g. B. 10 bar (preload of the spring 13); the moment F 2 times b has no influence on the further function.
  • the exemplary embodiment according to FIG. 3 differs from that according to FIG. 1 in that the controller interacts with a pump whose stroke volume decreases with increasing control pressure - see FIG. 4. This necessitates minor changes in the control device - in the same parts as before the same digits.
  • the change essentially consists only in the fact that the lever 20 is now constructed with one arm, specifically in that the pivot point 25 'lies below the effective direction of the forces F 2 and A times p st , and that the force F 2 is also greater than the force A times p st , otherwise the lever 20 would lift off the roller 27.
  • the auxiliary pressure is not generated by an auxiliary pump, but is branched off by the adjustable pump 10.
  • control pressure p st and spring force F 2 can also act on the control valve 16 from the other side.
  • the power level can be changed in a simple manner by changing the preload of the springs F (choice of the power hyperbola).
  • F 2 takes into account the value p 1 (see FIG. 4) of the pump characteristic.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Using the control apparatus according to Fig. 1, it is possible to keep the product of the volumetric delivery and outlet pressure of a variable-displacement pump (10) exactly constant. This is achieved when two oppositely directed moments must be brought into equilibrium on a lever (20), one moment being formed by a force (33) acting on a lever arm of constant length, and the other torque being formed by a force which is formed from a pressure acting on the end face (A) of a control valve (16) multiplied by the end area thereof and which acts on a lever arm (p) whose length is varied linearly in a manner proportional to the working pressure of the pump. The control pressure (pst) required to adjust the pump is formed at the control valve, which is operationally connected to the lever (20) and is controlled by the latter. It acts as a pressure-reducing valve in such a way that with increasing working pressure - depending on the design of the pump - a falling or rising control pressure is obtained with a hyperbolic shape, which adjusts the pump in accordance with a characteristic of constant torque. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Regeleinrichtung nach der Gattung des Hauptanspruchs. Bei einer derartigen bekannten druckproportional verstellbaren Pumpe ändert sich innerhalb eines bestimmten Bereiches des Steuerdrucks das Hubvolumen der Pumpe linear mit diesem Druck. Die Auslegung kann mit positivem oder negativem Gradienten erfolgen, d. h. bei steigendem Steuerdruck wird das Hubvolumen größer oder kleiner. Eine derartige Einrichtung hat den Nachteil, daß die die Pumpe antreibende Maschine überlastet werden kann.The invention relates to a control device according to the type of the main claim. In such a known pressure-proportionally adjustable pump, the stroke volume of the pump changes linearly with this pressure within a certain range of the control pressure. The design can be done with a positive or negative gradient, i. H. the stroke volume increases or decreases with increasing control pressure. Such a device has the disadvantage that the machine driving the pump can be overloaded.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Einrichtung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß mit ihr in Abhängigkeit vom Arbeitsdruck der Steuerdruck jeweils so gebildet wird, daß das Produkt aus Hubvolumen mal Arbeitsdruck der Pumpe konstant bleibt. Für konstante Antriebsdrehzahl bedeutet dies konstante Leistung an der Antriebsmaschine. Diese kann damit nicht überlastet werden. Wesentlich ist, daß die erfindungsgemäße Einrichtung eine exakte Leistungshyperbel erzeugt und eine einfache Veränderung des gewählten Leistungsniveaus erlaubt.The device according to the invention with the characterizing features of the main claim has the advantage that with it, depending on the working pressure Control pressure is formed so that the product of the stroke volume times the working pressure of the pump remains constant. For constant drive speed, this means constant power on the drive machine. This cannot be overloaded. It is essential that the device according to the invention generates an exact performance hyperbole and allows a simple change in the selected performance level.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Merkmale möglich. So kann es vorteilhaft sein, wenn der Steuerdruck nicht über eine Hilfspumpe erzeugt werden muß, sondern direkt aus dem Arbeitsdruck der Pumpe gewonnen werden kann.Advantageous further developments and improvements of the features specified in the main claim are possible through the measures listed in the subclaims. So it can be advantageous if the control pressure does not have to be generated by an auxiliary pump, but can be obtained directly from the working pressure of the pump.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein erstes Ausführungsbeispiel in schematischer Darstellung, Figur 2 ein Diagramm, Figur 3 ein zweites Ausführungsbeispiel, Figur 4 ein zweites Diagramm, Figur 5 ein drittes Ausführungsbeispiel wiederum in schematischer Darstellung.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a first exemplary embodiment in a schematic representation, FIG. 2 shows a diagram, FIG. 3 shows a second exemplary embodiment, FIG. 4 shows a second diagram, and FIG. 5 shows a third exemplary embodiment again in a schematic representation.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist mit 10 eine verstellbare Pumpe bezeichnet, deren Hubring 11 mittels eines druckbeaufschlagten Stellkolbens 12 entgegen einer Gegenkraft 13 zwecks Hubver- änderung der Kolben verstellbar ist. In die den Stellkolben 12 aufnehmende Bohrung 14 mündet eine Leitung 15, die von einem Ventil 16 herkommt. Das Ventil 16 ist symbolisch als 3/3-Wegeventil dargestellt, das zwischen den einzelnen Schaltstellungen I-III fließende oder stetige Übergänge aufweist. Dies ist symbolisch durch die zwei parallel verlaufenden Linien dargestellt.In FIG. 1, 10 denotes an adjustable pump, the stroke ring 11 of which can be adjusted by means of a pressurized actuating piston 12 against a counterforce 13 for the purpose of changing the stroke of the pistons. In the control piston 12 receiving bore 14 opens a line 15 which comes from a valve 16. The valve 16 is symbolically represented as a 3/3-way valve which has smooth or continuous transitions between the individual switching positions I-III. This is symbolically represented by the two parallel lines.

Von der Leitung 15 zweigt eine Leitung 18 ab, die zur linken Stirnseite A des Ventilschiebers führt. Dieser ist über eine Stange 19 oder einen Stößel an einem Hebel 20 angelenkt.A line 18 branches off from line 15 and leads to the left end A of the valve spool. This is articulated on a lever 20 via a rod 19 or a plunger.

Von einer Hilfspumpe 22 führt eine Leitung 23 zum Ventil 16, von diesem eine Leitung 24 zu einem Behälter 25.' Zwischen den Leitungen 23 und 24 ist ein Druckbegrenzungsventil 26' angeordnet.From an auxiliary pump 22, a line 23 leads to the valve 16 of this line 24 to a container 25 'between lines 23 and 24, a pressure limiting valve 26' is arranged.

Der Hebel 20 ist um einen Schwenkpunkt 25'schwenkbar. Die Lage des Schwenkpunkts wird vorgegeben durch eine an einer Kolbenstange 26 angeordneten Rolle 27. Der mit der Kolbenstange 26 verbundene Kolben 28 ist in einem Zylinder 29 geführt und über eine Leitung 30 vom Arbeitsdruck der Pumpe 10 entgegen der Kraft einer Feder 31 beaufschlagt.The lever 20 is pivotable about a pivot point 25 '. The position of the pivot point is predetermined by a roller 27 arranged on a piston rod 26. The piston 28 connected to the piston rod 26 is guided in a cylinder 29 and is acted upon by the working pressure of the pump 10 against the force of a spring 31 via a line 30.

Am Hebel 20 greift über einen stets konstanten Hebelarm a eine Feder 33 an; deren Vorspannung ist veränderbar. Bei einer bestimmten, konstant gehaltenen Federvorspannung übt sie über den Hebelarm a ein konstantes (rechtsdrehendes) Drehmoment auf den Hebel 20 aus. Diesem wirkt ein linksdrehendes Drehmoment entgegen, bestehend aus der Kraft A mal pst mal dem Hebelarm b (= p mal cf), wobei p t der Steuerdruck am Ausgang des Ventils 16 ist, p der Arbeitsdruck der Pumpe 10, c die Wirkfläche des Kolbens 28 geteilt durch die Federkonstante.der Feder 21.A spring 33 acts on the lever 20 via a constantly constant lever arm a; the preload is changeable. With a certain, constant spring preload, it exerts a constant (clockwise) torque on lever 20 via lever arm a. This acts levorotatory counterclockwise torque, consisting of the force A times p st times the lever arm b (= p · c f), wherein the control pressure pt at the output of the valve 16, p is the working pressure of the pump 10, the effective area c of the piston 28 divided by the spring constant of spring 21.

Der Kraft A mal pst wirkt eine Feder (Federkraft F2) entgegen, deren Wirkrichtung in Richtung der Kraft A mal pst verläuft. Am Hebel 20 herrscht Gleichgewicht, wenn

Figure imgb0001
daraus errechnet sich
Figure imgb0002
P ist die über die Vorspannung von F1 wählbare hydraulische Leistung der Pumpe 10. Daraus ist zu erkennen, daß der Steuerdruck eine Hyperbel ist - siehe hierzu Figur 2 - bzw. daß das Produkt aus Hubvolumen und Arbeitsdruck ebenfalls eine Hyperbel wird, wenn dieser Steuerdruck die Pumpe 11 druckproportional verstellt.The force A times p st is counteracted by a spring (spring force F 2 ) whose direction of action runs in the direction of the force A times p st . There is balance at lever 20, if
Figure imgb0001
from this is calculated
Figure imgb0002
P is the hydraulic power of the pump 10 which can be selected via the preload of F 1. From this it can be seen that the control pressure is a hyperbola - see FIG. 2 in this regard - or that the product of the stroke volume and working pressure also becomes a hyperbola if this control pressure the pump 11 is adjusted in proportion to the pressure.

Ein Regelvorgang sieht folgendermaßen aus: Steigt beispielsweise bei einem bestimmten Hubvolumen der Pumpe 10 der Arbeitsdruck p an, so wird der Kolben 28 entgegen der Kraft der Feder 31 verschoben, und der Hebelarm b wird größer. Damit wird auch das linksdrehende Moment A mal pst mal b größer und überwiegt das rechtsdrehende Moment F1 mal a. Der Hebel 20 schwenkt nun um den Schwenkpunkt 25' entgegen dem Uhrzeigersinn, wodurch das Ventil 16 aus seiner Neutralstellung II in Arbeitsstellung I verstellt wird. Dadurch kann Druckmittel aus der Bohrung 14 zum Behälter 25 abströmen. Die Feder 13 stellt dann die Pumpe auf geringere Fördermenge ein, und zwar so lange, bis das rechtsdrehende Moment infolge des geringer werdenden Druckes pst den Hebel 20 und damit das Ventil 16 wieder in seine vorherige Lage bringt.A control process looks like this: If, for example, the working pressure p rises at a certain stroke volume of the pump 10, the piston 28 is displaced against the force of the spring 31 and the lever arm b becomes larger. This means that the left-turning moment A times p st times b increases and outweighs the right-turning moment F 1 times a. The lever 20 now pivots counterclockwise about the pivot point 25 ', as a result of which the valve 16 is moved from its neutral position II into the working position I. This allows pressure medium to flow out of the bore 14 to the container 25. The spring 13 then adjusts the pump to a lower delivery rate, namely until the right-hand turning moment due to the decreasing pressure p st the lever 20 and thus that Brings valve 16 back to its previous position.

Herrscht wieder Gleichgewicht am Hebel und sinkt der Arbeitsdruck p, so verschiebt die Feder 31 den Kolben 28 derart, daß der Hebelarm b kleiner wird. Nunmehr überwiegt das rechtsdrehende Moment F1 mal a das Entgegengerichtete, wodurch der Hebel 20 um den Schwenkpunkt 25'im Uhrzeigersinn verschwenkt wird. Das Ventil 16 wird nun aus seiner Neutralstellung II in Arbeitsstellung III verstellt. Von der Hilfspumpe 22 gefördertes Druckmittel kann nunmehr in die Leitung 15 strömen und über den Stellkolben 12 die Pumpe auf größere Fördermenge einstellen. Damit wird der Kolben 28 wieder solange entgegen der Kraft der Feder 31 verschoben bis über die Kennlinie der Feder 31 wieder Gleichgewicht am Hebel 22 hergestellt ist.If there is equilibrium again on the lever and the working pressure p drops, the spring 31 displaces the piston 28 in such a way that the lever arm b becomes smaller. Now the clockwise torque F1 times a outweighs the opposite, whereby the lever 20 is pivoted clockwise about the pivot point 25 '. The valve 16 is now adjusted from its neutral position II to working position III. Pressure medium delivered by the auxiliary pump 22 can now flow into the line 15 and adjust the pump to a larger delivery rate via the actuating piston 12. Thus, the piston 28 is again moved against the force of the spring 31 until the spring 22 is again at balance on the lever 22.

Das Ventil 16 wirkt als Druckminderventil mit stetigem Übergang zwischen Sperrstellung und den Arbeitsstellungen I und III. Der von der Hilfspumpe 22 erzeugte Druck Ph wird durch das Ventil in den Druck Pst umgewandelt - siehe hierzu die obigen Formeln.The valve 16 acts as a pressure reducing valve with a continuous transition between the blocking position and the working positions I and III. The pressure Ph generated by the auxiliary pump 22 is converted by the valve into the pressure Pst - see the formulas above.

Auf diese Weise wird die Pumpe 10 so eingestellt, daß das Produkt aus Fördervolumen und Arbeitsdruck stets konstant ist, d. h. diese Werte bilden eine exakte Hyperbel.In this way, the pump 10 is set so that the product of the delivery volume and working pressure is always constant, i. H. these values form an exact hyperbola.

Die Kraft F2 am Hebelarm b, die po entspricht, bewirkt eine Ausstellung der Pumpe erst ab einem bestimmten Druck, z. B. 10 bar (Vorspannung der Feder 13); auf die weitere Funktion hat das Moment F2 mal b keinen Einfluß.The force F 2 on the lever arm b, which corresponds to p o , causes the pump to be released only at a certain pressure, e.g. B. 10 bar (preload of the spring 13); the moment F 2 times b has no influence on the further function.

Das Ausführungsbeispiel nach Figur 3 unterscheidet sich von demjenigen nach Figur 1 dadurch, daß hier der Regler mit einer Pumpe zusammenwirkt, deren Hubvolumen bei steigendem Steuerdruck abnimmt - siehe hierzu Figur 4. Dies bedingt geringfügige Änderungen in der Regeleinrichtung - in der gleiche Teile wie zuvor mit denselben Ziffern bezeichnet sind. Die Änderung besteht im wesentlichen nur darin, daß nun der Hebel 20 einarmig ausgebildet ist, und zwar dadurch, daß der Schwenkpunkt 25'unterhalb der Wirkrichtung der Kräfte F2 und A mal pst liegt, und daß auch die Kraft F2 größer ist als die Kraft A mal pst, denn sonst würde sich der Hebel 20 von der Rolle 27 abheben. Somit ist bei Kräftegleichgewicht

Figure imgb0003
und damit
Figure imgb0004
Im obigen Ausführungsbeispiel wird der Hilfsdruck nicht von einer Hilfspumpe erzeugt, sondern er wird von der verstellbaren Pumpe 10 abgezweigt.The exemplary embodiment according to FIG. 3 differs from that according to FIG. 1 in that the controller interacts with a pump whose stroke volume decreases with increasing control pressure - see FIG. 4. This necessitates minor changes in the control device - in the same parts as before the same digits. The change essentially consists only in the fact that the lever 20 is now constructed with one arm, specifically in that the pivot point 25 'lies below the effective direction of the forces F 2 and A times p st , and that the force F 2 is also greater than the force A times p st , otherwise the lever 20 would lift off the roller 27. Thus there is a balance of forces
Figure imgb0003
and thus
Figure imgb0004
In the above embodiment, the auxiliary pressure is not generated by an auxiliary pump, but is branched off by the adjustable pump 10.

Das Ausführungsbeispiel nach Figur 5 zeigt, daß Steuerdruck pst und Federkraft F2 auch jeweils von der anderen Seite her am Steuerventil 16 einwirken können.The embodiment of Figure 5 shows that control pressure p st and spring force F 2 can also act on the control valve 16 from the other side.

Durch Verändern der Vorspannung der Federn F kann das Leistungsniveau auf einfache Weise verändert werden (Wahl der Leistungshyperbel). Mit F2 wird der Wert p1 (siehe Figur 4) der Pumpenkennlinie berücksichtigt.The power level can be changed in a simple manner by changing the preload of the springs F (choice of the power hyperbola). F 2 takes into account the value p 1 (see FIG. 4) of the pump characteristic.

Claims (9)

1. Regeleinrichtung für eine verstellbare Pumpe mit einem Steuerventil, das Druckmittel unter einem Steuerdruck zu einem das Verstellorgan (Schwenkscheibe, Hubring) der Pumpe einstellenden Kolben leitet, dadurch gekennzeichnet, daß der Steuerdruck auf die Stirnseite (A) des Steuerventilschiebers (16) einwirkt und die so erzeugte erste Kraft an einem Hebel (20) über einen Hebelarm (b) einwirkt, dessen Länge sich linear proportional dem Arbeitsdruck der Pumpe 10 ändert, und daß diesem Moment ein zweites Moment am Hebel entgegenwirkt, das gebildet ist aus einer an einem Hebelarm (a) mit konstanter Länge angreifenden Kraft (F1).1. Control device for an adjustable pump with a control valve, the pressure medium passes under a control pressure to a the adjusting member (swivel plate, cam ring) of the pump adjusting piston, characterized in that the control pressure acts on the end face (A) of the control valve spool (16) and the first force thus generated acts on a lever (20) via a lever arm (b), the length of which changes linearly in proportion to the working pressure of the pump 10, and this moment is counteracted by a second moment on the lever, which is formed from one on a lever arm (a) Force applied with constant length (F1). 2. Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der vom Steuerventilschieber auf den Hebel (20) ausgeübten Kraft eine Kraft (F2) entgegenwirkt, die insbesondere in derselben Wirkrichtung verläuft.2. Device according to claim 1, characterized in that the force exerted by the control valve slide on the lever (20) counteracts a force (F2) which extends in particular in the same direction of action. 3. Einrichtung nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß der Hebel zweiarmig ausgebildet ist und die zweite Kraft durch eine Feder (34) erzeugt wird.3. Device according to claim 1 and / or 2, characterized in that the lever is formed with two arms and the second force is generated by a spring (34). 4. Einrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der veränderliche Hebelarm (b) dadurch gebildet wird, daß der Hebel (20) an einem Schwenkpunkt (25') anliegt, der am Ende einer Kolbenstange (26) liegt, deren Kolben (28) vom Arbeitsdruck der verstellbaren Pumpen (10) beaufschlagt ist.4. Device according to one of claims 1 to 3, characterized in that the variable lever arm (b) is formed in that the lever (20) abuts a pivot point (25 ') which is located at the end of a piston rod (26), whose piston (28) is acted upon by the working pressure of the adjustable pumps (10). 5. Einrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das Steuerventil (16) als Druckminderventil mit stetigem Übergang zwischen den einzelnen Schaltstellungen ausgebildet ist.5. Device according to one of claims 1 to 4, characterized in that the control valve (16) is designed as a pressure reducing valve with a continuous transition between the individual switching positions. 6. Einrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Hebel einarmig ausgebildet ist.6. Device according to one of claims 1 to 5, characterized in that the lever is formed with one arm. 7. Einrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Hebel zweiarmig, ausgebildet ist.7. Device according to one of claims 1 to 5, characterized in that the lever is formed with two arms. 8. Einrichtung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß der Steuerdruck aus dem von einer Hilfspumpe (22) geförderten Druckmittelstrom gebildet wird.8. Device according to one of claims 1 to 7, characterized in that the control pressure is formed from the pressure medium flow delivered by an auxiliary pump (22). 9. Einrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß der Steuerdruck aus dem von der verstellbaren Pumpen selbst geförderten Druckmittel abgezweigt wird.9. Device according to one of claims 1 to 8, characterized in that the control pressure is branched off from the pressure medium delivered by the adjustable pumps themselves.
EP83103940A 1982-05-08 1983-04-22 Control apparatus for a variable displacement pump Withdrawn EP0093916A1 (en)

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DE19823217360 DE3217360A1 (en) 1982-05-08 1982-05-08 CONTROL DEVICE FOR AN ADJUSTABLE PUMP
DE3217360 1982-05-08

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Publication number Priority date Publication date Assignee Title
EP0939225A3 (en) * 1998-02-26 2000-06-14 Brueninghaus Hydromatik Gmbh Power control circuit for a plurality of hydrostatic variable displacement pumps
EP1304482A2 (en) * 2001-10-18 2003-04-23 Brueninghaus Hydromatik Gmbh Total power controller
FR2931522A1 (en) * 2008-05-26 2009-11-27 Snecma Linear actuator for e.g. variable bleed valve, of jet engine of airplane or aircraft, has pivot actuator displacing movable pivot with respect to lever according to received set point so that intensity of actuating force is varied

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6133982U (en) * 1984-07-31 1986-03-01 三菱重工業株式会社 Constant force type flow control device
JPS61149789U (en) * 1985-03-08 1986-09-16
JPS61184888U (en) * 1985-05-13 1986-11-18
JPS62243978A (en) * 1986-04-14 1987-10-24 Uchida Yuatsu Kiki Kogyo Kk Delivery amount control device for variable displacement oil hydraulic pump

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1528530A1 (en) * 1965-08-27 1969-08-21 Von Roll Ag Hydraulic control device
US3669570A (en) * 1970-03-09 1972-06-13 Mannesmann Meer Ag Power regulation for fluid machines
DE2146544A1 (en) * 1971-09-17 1973-03-29 Hans Dipl Ing Molly DEVICE FOR REGULATING SIZES THAT ARE GIVEN BY THE PRODUCT OF TWO MEASURED VALUES
US3864063A (en) * 1973-09-11 1975-02-04 Cessna Aircraft Co Automatic torque limitation control
DE2362093A1 (en) * 1973-12-14 1975-06-19 Bosch Gmbh Robert Adjustable pump regulating installation - is to keep pressure and volume constant with pressure acting on a regulating lever
DE2419460A1 (en) * 1974-04-23 1975-11-06 Bosch Gmbh Robert Radial piston pump regulator - has opposite displacement ring a counter piston subjected to discharge pressure
USRE29333E (en) * 1969-04-23 1977-08-02 Massey-Ferguson Services N.V. Hydraulic apparatus for regulating the flow of one or more pumps
DE2942403A1 (en) * 1979-10-19 1981-04-30 Linde Ag, 6200 Wiesbaden Volume control for hydraulic pump - has mechanical linkage to give hyperbolic relationship between discharge pressure and volume

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1528530A1 (en) * 1965-08-27 1969-08-21 Von Roll Ag Hydraulic control device
USRE29333E (en) * 1969-04-23 1977-08-02 Massey-Ferguson Services N.V. Hydraulic apparatus for regulating the flow of one or more pumps
US3669570A (en) * 1970-03-09 1972-06-13 Mannesmann Meer Ag Power regulation for fluid machines
DE2146544A1 (en) * 1971-09-17 1973-03-29 Hans Dipl Ing Molly DEVICE FOR REGULATING SIZES THAT ARE GIVEN BY THE PRODUCT OF TWO MEASURED VALUES
US3864063A (en) * 1973-09-11 1975-02-04 Cessna Aircraft Co Automatic torque limitation control
DE2362093A1 (en) * 1973-12-14 1975-06-19 Bosch Gmbh Robert Adjustable pump regulating installation - is to keep pressure and volume constant with pressure acting on a regulating lever
DE2419460A1 (en) * 1974-04-23 1975-11-06 Bosch Gmbh Robert Radial piston pump regulator - has opposite displacement ring a counter piston subjected to discharge pressure
DE2942403A1 (en) * 1979-10-19 1981-04-30 Linde Ag, 6200 Wiesbaden Volume control for hydraulic pump - has mechanical linkage to give hyperbolic relationship between discharge pressure and volume

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0939225A3 (en) * 1998-02-26 2000-06-14 Brueninghaus Hydromatik Gmbh Power control circuit for a plurality of hydrostatic variable displacement pumps
EP1304482A2 (en) * 2001-10-18 2003-04-23 Brueninghaus Hydromatik Gmbh Total power controller
EP1304482A3 (en) * 2001-10-18 2005-09-07 Brueninghaus Hydromatik Gmbh Total power controller
FR2931522A1 (en) * 2008-05-26 2009-11-27 Snecma Linear actuator for e.g. variable bleed valve, of jet engine of airplane or aircraft, has pivot actuator displacing movable pivot with respect to lever according to received set point so that intensity of actuating force is varied

Also Published As

Publication number Publication date
JPS58195088A (en) 1983-11-14
DE3217360A1 (en) 1983-11-10
JPH0459471B2 (en) 1992-09-22

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