EP0284987B1 - Regulator for at least two hydrostatic machines linked to a common pressure pipe - Google Patents

Regulator for at least two hydrostatic machines linked to a common pressure pipe Download PDF

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Publication number
EP0284987B1
EP0284987B1 EP88104660A EP88104660A EP0284987B1 EP 0284987 B1 EP0284987 B1 EP 0284987B1 EP 88104660 A EP88104660 A EP 88104660A EP 88104660 A EP88104660 A EP 88104660A EP 0284987 B1 EP0284987 B1 EP 0284987B1
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EP
European Patent Office
Prior art keywords
pressure
valve
control
regulator
regulating device
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EP88104660A
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German (de)
French (fr)
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EP0284987A2 (en
EP0284987A3 (en
Inventor
Gerhard Beutler
Hermann Maier
Clemens Krebs
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Brueninghaus Hydraulik GmbH
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Brueninghaus Hydraulik GmbH
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    • 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.
  • the delivery rate settings of the pumps are indefinite because, due to the approximately constant working pressure, no relationship can be derived which would allow a uniform delivery rate setting for all pumps, i.e. enables parallel operation. Therefore, the pumps can take any delivery settings at any time, e.g. one pump can be in maximum and the other pump in minimum delivery setting. This has the following disadvantages.
  • the pumps oscillate at a swivel angle, even if the total amount delivered does not change. This results in losses and noises.
  • the pumps are deliberately set to slightly different controller characteristics.
  • the first pump regulates eg at 200 bar, the second at 205 bar and the third at 210 bar.
  • the load is thus clearly defined and the pendulum is avoided, although the pumps are subject to different wear due to different loads.
  • an increase in pressure in stages is predetermined in this known method.
  • the invention is based on the object of designing a control device of the type described at the outset in such a way that hydraulic synchronous operation or parallel operation is achieved while ensuring uniform loading of the machines with one another.
  • an additional control signal is included in the control, which is generated as a function of the volume setting of the machines and which is given to the associated controllers as an average setpoint.
  • the achieved by the inventive design synchronization of the pump results from the fact that each controller is supplied with a correction signal in dependence of the (position) deviation X is -X is to be formed, of each of the volume setting of the associated machine essentially linearly dependent control signal and the setpoint signal formed as the mean value of the control signals. There is no significant increase in pressure in the controller characteristic curve, because this is reduced again by regulating the pumps to the same delivery rate.
  • the solution according to the invention is characterized by low losses.
  • the embodiment according to claim 6 leads to a simple and practical construction in machines with reversible throughput direction.
  • the design according to claim 8 includes simple and practical features for remote control of the pressure regulator.
  • the pumps denoted by 1 are connected by line sections 2 to a common working pressure line 3 leading to a consumer B, the number of pumps being able to be increased as desired, which is illustrated by the position symbol 4, which denotes connections for further possible pumps.
  • the pump units are identical to one another.
  • Each adjusting device 5 of the pumps 1 is assigned a pressure regulator 6 with a first proportional control valve 7 in the form of a pressure compensator, the slide 8 of which regulates the passage of a connecting line 9 which starts from the associated working pressure line section 2 and into the piston chamber 10 of a cylinder 11 of the adjusting device 5 flows.
  • the slide 8 is acted upon by a line section 12 with the working pressure against a valve spring 15, the spring force of which is optionally adjustable.
  • the piston annular space 16 of the cylinder 11, in which a compression spring 17 is arranged for the purpose of resetting the adjusting device 5, is connected to the connecting line 9 by a line section 18 and can thus be subjected to the working pressure.
  • the pressure regulator 6 described so far including an adjustable nozzle, designated 19, in a discharge line 20 extending from the piston chamber 10 and a parallel line 21 connected to the latter and originating from the control valve 7 is of a conventional design and is therefore known, so that a functional description can be dispensed with in detail. It should be emphasized that the pressure regulators 6 set a working pressure which, apart from a slight change in pressure, can be regarded as essentially constant. The slight change in pressure in the working pressure in the control range of the pressure regulator 6 is due to the progressive characteristic curve of the springs 15 and 17, as well as to the friction and self-adjusting forces of the adjusting device 5, and is about 3 bar in the case of conventional pressure regulators 6.
  • each pump 1 is assigned a control means, generally designated 25, which acts on a second control valve 37 to be described with a control signal which is dependent on the respective delivery rate setting of the associated pump 1 and with a setpoint signal common to all pumps.
  • the control means 25 is formed by a pressure relief valve 26, which is arranged in a line 27, which continues from the outlet of the pressure relief valve 26 as a discharge line 28, and which branches off behind a throttle 29 from a line 30 which starts from the connecting line 9 containing the working pressure .
  • the control means 25 generates in the beginning after the restrictor 29 section 31 of the line 30 a depending on the particular delivery setting of the associated pump 1 control signal X is.
  • An actuator 32 in the form of a plunger or stylus 33 is used to transmit the respective setting corresponding to the delivery quantity setting, which abuts at one end an inclined surface 35 present on the adjusting piston 34 of the cylinder 11 outside the latter and acts on the slide of the pressure relief valve 26 by means of a spring 36 and applied against the inclined surface 35 is.
  • the adjusting element 32 is displaceably mounted in its longitudinal direction, so that when the adjusting piston 34 is adjusted longitudinally, it performs a longitudinal movement which adjusts the pressure limiting valve.
  • the aforementioned second control valve (proportional control valve), designated 37 is arranged in the form of a pressure compensator, the slide 38 of which is connected on the one hand by a line section 39 to the line 30 and on the other hand by a line section 41 to a connecting line 42, to which the control valve 37 associated with the other pump 1 or all the existing control valves 37 are also connected by means of the line sections 41.
  • the line 30 and the connecting line 42 are short-circuited in the region of each control valve 37 by a connecting line 43 which circumvents the latter and in which a throttle 44 is arranged.
  • the throttles 44 generate a control signal X soll in the connecting line 42, which is common to all the control valves 37.
  • the slide 38 of which is acted upon on both sides by a valve spring 45, 46, of which the spring force of the valve spring 46 is adjustable, the pressure signals X is and X is to be weighed against one another, as a result of which the control valve 37 is in line 47 correction signal X K generated, which the control valve 7 is a control deviation X is -X is to be signaled.
  • the line 48 can be loaded externally with any pressure or, in a simplified manner, be connected to the line section 31 at the node 49. A connection of line 48 to line 9 would also be possible, similar to the embodiment to be described in FIG. 3.
  • the arrangement is such that the pressure relief valve 26 opens when the adjusting device 5 is pivoted in, ie during an adjusting movement of the adjusting piston 34 to the left, as a result of which the control signal X is or the control pressure present in the connecting line 31 is reduced, ie it becomes a this adjustment is degressive pressure signal X and generated by means of the control valve 37 a progressive pressure signal X m.
  • the latter acts on the slide 8 of the control valve 7 against the working pressure.
  • the working pressure at the control valve 7 is no longer only in equilibrium with the force of the spring 15 (controller setting), but the controller setting increases as a function of the control deviation X ist -X soll by the pressure signal X K.
  • the total delivery rate setting of the pumps 1 is determined by the essentially equal working pressure acting on the pressure regulator 6.
  • the desired even distribution of flow to the pump 1 is of the deviation of the respective pressure signal X to the common average pressure signal X and the resulting impact on the control valves 7 determined by the correction signal X K.
  • the configuration according to the invention is suitable for pumps which can be set in both delivery directions.
  • the first control valves 7 are connected to a common remote control valve 52, which can be formed by a pressure limiting valve.
  • the second control valves 51 are formed by adjustable throttles 53, which are each arranged in line sections 54, which originate from line sections 55 holding the control signal X K and lead to a common connecting line 56 connected to the outlet, in which the remote control valve 52 is arranged.
  • An essential difference from the first exemplary embodiment is that the line sections 55 containing the control signal X K are connected directly to the connecting line 9 containing the working pressure via line sections 57 with throttles 58.
  • valve 51 immediate connection line 59 provided with a throttle 60, to which is the pressure signal X and to the pressure signal X containing lines 31 are connected 42 also in the embodiment of Fig. 2, wherein the slide of the control valve 51 by comparable with the embodiment according to FIG. 1 line sections 61, 62 on the one hand is connected to the pressure signal X, and on the other hand to the pressure signal X is simultaneously acted upon.
  • valve springs 63, 64 are provided on both sides of the slide, of which the valve spring 64 is adjustable.
  • the pressure limiting valve 26 opens when the adjusting device 5 is pivoted in by a certain amount, as a result of which the pressure signal X ist is generated by pressure relief in the line section 31. Due to the pressure relief, the slide of the control valve 51 is shifted slightly to the left, as a result of which the passage in the control valve 51 is throttled and an increasing pressure is built up in the line section 55, which progressively acts on the slide 8 of the control valve 6 to support the force of the valve spring 15, as a result of which the pressure increase in the controller characteristic is reached.
  • the total delivery rate setting of the pumps 1 is determined by the essentially equal working pressure acting on the pressure regulator 6.
  • the desired even distribution of flow to the pump 1 is of the deviation of the respective pressure signal X to the common average pressure signal X and the resulting impact on the control valves 7 determined by the correction signal X K.
  • the or all control valves 7 or pressure regulator 6 can be controlled simultaneously with only one control element.
  • a control valve 71 is arranged in the connecting line 9 connecting the working pressure line to the piston chamber 10 of the cylinder 11 of the adjusting device 5, the slide 72 of which, on the one hand, is connected to that of the pressure relief valve 26 set pressure signal X, and on the other hand to the averaged pressure signal X can be acted upon, and that in principle corresponds to 37 in FIG. 1 the second control valve.
  • control valve 71 immediate connection line 43 is provided with the restrictor 44, on the one hand to the pressure signal X should compound containing line 42, and on the other hand connected to the containing the working pressure connection pipe 9 via the restrictor 29th
  • the slide 72 of the control valve 71 is also acted upon on both sides by the forces of valve springs 73, 74, the force of the valve spring 74 being adjustable.
  • a control valve 76 which is common to all pumps 1 is provided and which is arranged in a line 77 branching off from the working pressure line 3, from which to each adjusting device 5
  • Line section 78 branches off with a throttle 79, which is between the control valve 71 and Piston chamber 10 of the adjusting device 5 is connected to the connecting line 9.
  • the control valve 76 thereby regulates the pressure in the piston chamber 10 of all pumps and thus the adjustment device 5 of all pumps simultaneously.
  • the pressure signal X ist is weighed against the averaged pressure signal X soll at the control valve 71 and the valve slide 72 assumes a position dependent on the control deviation X ist -X soll .
  • control valve 76 which is a pressure control valve in the present exemplary embodiment, is acted upon by the line section 82 connected to the working pressure line 3 against a valve spring 83 with working pressure.
  • control valves 37, 51 and 71 are centered on the center due to the action of valve springs on both sides. They are thus able on the one hand and / or on the other hand to process signals effective pressure, which is depending on the size of the existing control deviation X -X should effected.
  • a throttle 84 or 85 is assigned to the control valve 71 both on the input side and on the output side toward the outlet.
  • FIG. 4 shows, as an exemplary embodiment, a sectional view of a pressure limiting valve 26 in an enlarged view.
  • the actuating element 32 acts on the one hand her makeup CDn and on the other hand engaging on the slide 87 spring 88 on the slider 87 of the pressure relief valve 26, which is the control signal X by means of control edges 89 that is, the slider 87 regulates acting control pressure.
  • the valve housing 93 is screwed into the housing of the cylinder 11 or an attachment part of the same.
  • the slide 87 is located in an adjusting bush 94, which can be adjusted axially in the valve housing 93 by means of a thread 95 by turning an attack element, here a hexagon socket 96, and can be locked by means of a lock nut 97 screwed onto the adjusting bush 94.
  • port 98 e.g. 1 and 2 can be connected to the line 27, and a transverse bore 99 which intersects the bore 91 in the adjusting bush 94 and which corresponds to the line 27, an input throttle 100 is arranged which corresponds to the throttles 29.
  • the line 31 can be connected to the connection 101.

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

Description

Die Erfindung bezieht sich auf eine Regeleinrichtung nach dem Oberbegriff des Anspruchs 1.The invention relates to a control device according to the preamble of claim 1.

Wenn mehrere geregelte, insbesondere druckgeregelte Pumpen gemeinsam in eine Arbeitsdruckleitung bzw. ein Verbrauchernetz im wesentlichen konstanten Druckes speisen, sind die Fördermengeneinstellungen der Pumpen unbestimmt, weil sich aufgrund des in etwa konstanten Arbeitsdrucks keine Beziehung herleiten läßt, die eine gleichmäßige Fördermengeneinstellung bei allen Pumpen, d.h. den Parallelbetrieb ermöglicht. Deshalb können die Pumpen zu jeder Zeit beliebige Fördermengeneinstellungen einnehmen, z.B. kann eine Pumpe in maximaler und die andere Pumpe in minimaler Fördermengeneinstellung stehen. Dies hat folgende Nachteile.If several regulated, in particular pressure-controlled pumps feed together into a working pressure line or a consumer network of essentially constant pressure, the delivery rate settings of the pumps are indefinite because, due to the approximately constant working pressure, no relationship can be derived which would allow a uniform delivery rate setting for all pumps, i.e. enables parallel operation. Therefore, the pumps can take any delivery settings at any time, e.g. one pump can be in maximum and the other pump in minimum delivery setting. This has the following disadvantages.

Die Belastung und damit der Verschleiß sind ungleichmäßig verteilt.The load and thus the wear are distributed unevenly.

Jeder Pumpenantrieb muß auf Maximalleistung und 100 % Einschaltdauer ausgelegt werden, auch wenn die Maximalleistung selten erreicht wird.Every pump drive must be designed for maximum output and 100% duty cycle, even if the maximum output is rarely reached.

Die Pumpen pendeln im Schwenkwinkel, auch wenn die geförderte Gesamtmenge sich nicht ändert. Das hat Verluste und Geräusche zur Folge.The pumps oscillate at a swivel angle, even if the total amount delivered does not change. This results in losses and noises.

Im sogenannten Mooringbetrieb kann bei Verbrauchermenge Q = O eine Pumpe in positiver maximaler Fördermengeneinstellung und eine zweite in negativer maximaler Fördermengeneinstellung stehen. Dabei schluckt die zweite Pumpe die Fördermenge, die die erste fördert. Das hat einen erhöhten Verschleiß sowie Verlustleistung zur Folge und ist mit hoher Geräuschentwicklung verbunden.In so-called mooring operation, if the consumer quantity Q = O, one pump can be in the positive maximum delivery rate setting and a second in negative maximum delivery rate setting. The second pump swallows the flow rate that the first pump delivers. This results in increased wear and power loss and is associated with high noise levels.

Es ist bekannt, wenigstens zwei in eine gemeinsame Arbeitsdruckleitung bzw. ein gemeinsames Verbrauchernetz speisende Pumpen veränderlicher Fördermenge durch ein mechanisches Gestänge zum Gleichlauf- bzw. Parallelbetrieb zu zwingen. Diese Maßnahme führt nicht nur zu Leistungsverlusten, sondern es ist auch eine aufwendige stabile Mechanik notwendig. Außerdem ergibt sich bei dieser Ausgestaltung eine große und sperrige Bauweise, wodurch die räumliche Anordnung am Verwendungsort erschwert wird und insbesondere eine Anordnung der Pumpen in verhältnismäßig geringem Abstand voneinander vorgegeben ist.It is known to force at least two pumps of variable flow rate that feed into a common working pressure line or a common consumer network by means of a mechanical linkage for synchronous or parallel operation. This measure not only leads to a loss of performance, but also requires complex, stable mechanics. In addition, this configuration results in a large and bulky construction, which makes the spatial arrangement at the place of use difficult and, in particular, an arrangement of the pumps at a relatively short distance from one another is predetermined.

Eine andere bekannte, und zwar hydraulische, Methode, wenigstens zwei Pumpen annähernd gleichmäßig zu betreiben, d.h., den Verschleiß und die Belastung auf die Pumpen über die Zeit gleichmäßig zu verteilen, ist die sogenannte Kaskadenregelung. Bei dieser Maßnahme werden die Pumpen bewußt auf etwas unterschiedliche Reglerkennlinien eingestellt. Die erste Pumpe regelt z.B. bei 200 bar, die zweite bei 205 bar und die dritte bei 210 bar ein. Damit ist die Belastung eindeutig definiert und das Pendeln wird vermieden, wobei jedoch aufgrund unterschiedlicher Belastung der Pumpen letztere einem unterschiedlichen Verschleiß unterliegen. Um einen gleichmäßigen Verschleiß zu erreichen, ist es erforderlich, z.B. ein mal pro Woche die Einstellung der Pumpen zyklisch zu vertauschen. Außerdem ist bei dieser bekannten Methode ein Druckanstieg in Stufen vorgegeben.Another known, namely hydraulic, method of operating at least two pumps approximately evenly, ie distributing the wear and the load on the pumps evenly over time, is the so-called cascade control. With this measure, the pumps are deliberately set to slightly different controller characteristics. The first pump regulates eg at 200 bar, the second at 205 bar and the third at 210 bar. The load is thus clearly defined and the pendulum is avoided, although the pumps are subject to different wear due to different loads. In order to achieve even wear, it is necessary, for example, to set the pumps cyclically once a week to swap. In addition, an increase in pressure in stages is predetermined in this known method.

Der Erfindung liegt die Aufgabe zugrunde, eine Regeleinrichtung der eingangs bezeichneten Art so auszugestalten, daß bei Gewährleistung einer gleichmäßigen Belastung des Maschinen untereinander ein hydraulischer Gleichlaufbetrieb bzw. Parallelbetrieb erreicht wird.The invention is based on the object of designing a control device of the type described at the outset in such a way that hydraulic synchronous operation or parallel operation is achieved while ensuring uniform loading of the machines with one another.

Diese Aufgabe wird durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst.This object is achieved by the characterizing features of claim 1.

Bei der erfindungsgemäßen Ausgestaltung wird in die Regelung ein zusätzliches Steuersignal einbezogen, das in Abhängigkeit von der Volumeneinstellung der Maschinen erzeugt und als mittlerer Sollwert dem zugehörigen Reglern aufgegeben wird. Hierdurch wird ein Regelkriterium geschaffen, das bei jeweils gleichem auf die vorhandenen Regler wirksamen Arbeitsdruck die Regelung der Maschinen auf gleiche Volumeneinstellung ermöglicht. Der durch die erfindungsgemäße Ausgestaltung erzielte Gleichlauf der Pumpen ergibt sich daraus, daß jeder Regler mit einem Korrektursignal beaufschlagt ist, das in Abhängigkeit der (Lage-)Regelabweichung Xist-Xsoll gebildet ist, die von dem von der jeweiligen Volumeneinstellung der zugehörigen Maschine im wesentlichen linear abhängigen Steuersignal und dem als Mittelwert der Steuersignale gebildeten Sollwertsignal abhängig ist. Ein wesentlicher Druckanstieg in der Reglerkennlinie findet nicht statt, weil ein solcher durch das Ausregeln der Pumpen auf gleiche Fördermenge wieder abgebaut wird.In the embodiment according to the invention, an additional control signal is included in the control, which is generated as a function of the volume setting of the machines and which is given to the associated controllers as an average setpoint. This creates a control criterion that enables the machines to be regulated to the same volume setting with the same working pressure acting on the existing regulators. The achieved by the inventive design synchronization of the pump results from the fact that each controller is supplied with a correction signal in dependence of the (position) deviation X is -X is to be formed, of each of the volume setting of the associated machine essentially linearly dependent control signal and the setpoint signal formed as the mean value of the control signals. There is no significant increase in pressure in the controller characteristic curve, because this is reduced again by regulating the pumps to the same delivery rate.

Die erfindungsgemäße Lösung zeichnet sich durch geringe Verluste aus.The solution according to the invention is characterized by low losses.

Es ist aufgrund des Vorhandenseins einer progressiven Federkennlinie zwar auch bei bekannten Druckreglern eine leicht progressive Reglerkennlinie vorhanden, jedoch ist dies federspezifisch vorgegeben, und von Reibung und Eigenstellkräften abhängig und daher für eine Reglerrückführung unbrauchbar.Due to the presence of a progressive spring characteristic there is a slightly progressive regulator characteristic even with known pressure regulators, but this is spring-specific and dependent on friction and self-actuating forces and therefore unusable for regulator feedback.

Es ist zwar auch bekannt, bei einer sogenannten Momentenregelung den Regler in Abhängigkeit vom Arbeitsdruck und der Volumeneinstellung der Maschine zu regeln, jedoch erfolgt dies unter völlig anderen Voraussetzungen und auch zu einem völlig anderen Zweck, nämlich zur Erreichung eines günstigen Drehmomentes, wobei mit Federsätzen eine Reglerkennlinie in Form einer Hyperbel angestrebt wird, während bei der erfindungsgemäßen Ausgestaltung eine Reglerkennlinie in wesentlichen ohne Druckanstieg ergibt.It is also known to regulate the controller depending on the working pressure and the volume setting of the machine in a so-called torque control, but this takes place under completely different conditions and also for a completely different purpose, namely to achieve a favorable torque, one with spring sets Regulator characteristic curve in the form of a hyperbola is desired, while in the embodiment according to the invention a regulator characteristic curve results essentially without an increase in pressure.

Gemäß den Ansprüchen 2 bis 5 wird auf bewährte Maßnahmen zur Erzeugung eines Steuersignals in Abhängigkeit von der Volumeneinstellung der Maschine zurückgegriffen.According to claims 2 to 5, tried and tested measures for generating a control signal depending on the volume setting of the machine are used.

Die Ausgestaltung nach Anspruch 6 führt zu einer einfachen und praktikablen Bauweise bei Maschinen mit umkehrbarer Durchsatzrichtung.The embodiment according to claim 6 leads to a simple and practical construction in machines with reversible throughput direction.

Die Ausbildung nach Anspruch 8 umfaßt einfache und praktikable Merkmale für eine Fernsteuerung des Druckreglers.The design according to claim 8 includes simple and practical features for remote control of the pressure regulator.

Nachfolgend wird die Erfindung anhand von in vereinfachten Zeichnungen dargestellten bevorzugten Ausführungsbeispielen näher erläutert. Es zeigt:

Fig. 1
eine hydraulische Antriebseinheit mit zwei in eine gemeinsame Arbeitsdruckleitung speisende Pumpen, die durch eine erfindungsgemäße Regeleinrichtung für den Parallelbetrieb geregelt sind;
Fig. 2 und 3
abgewandelte Ausgestaltungen der Antriebseinheit;
Fig. 4
ein Steuermittel in Form eines Druckbegrenzungsventils in vergrößerter Schnittdarstellung.
The invention is explained in more detail below on the basis of preferred exemplary embodiments illustrated in simplified drawings. It shows:
Fig. 1
a hydraulic drive unit with two in a common working pressure line feeding pumps, which are regulated by a control device according to the invention for parallel operation;
2 and 3
modified configurations of the drive unit;
Fig. 4
a control means in the form of a pressure relief valve in an enlarged sectional view.

Die mit 1 bezeichneten Pumpen sind durch Leitungsabschnitte 2 mit einer zu einem Verbraucher B führenden gemeinsamen Arbeitsdruckleitung 3 verbunden, wobei die Anzahl der Pumpen beliebig vergrößert werden kann, was mit dem Positionszeichen 4 verdeutlicht ist, das Anschlüsse für weitere mögliche Pumpen bezeichnet. Die Pumpeneinheiten sind einander gleich ausgebildet.The pumps denoted by 1 are connected by line sections 2 to a common working pressure line 3 leading to a consumer B, the number of pumps being able to be increased as desired, which is illustrated by the position symbol 4, which denotes connections for further possible pumps. The pump units are identical to one another.

Jeder Verstellvorrichtung 5 der Pumpen 1 ist ein Druckregler 6 mit einem ersten Proportional-Regelventil 7 in Form einer Druckwaage zugeordnet, dessen Schieber 8 den Durchgang einer Verbindungsleitung 9 regelt, die vom zugehörigen Arbeitsdruckleitungsabschnitt 2 ausgeht und in den Kolbenraum 10 eines Zylinders 11 der Verstellvorrichtung 5 mündet. Hierzu ist der Schieber 8 durch einen Leitungsabschnitt 12 mit den Arbeitsdruck gegen eine Ventilfeder 15 beaufschlabgar, deren Federkraft wahlweise einstellbar ist. Der Kolbenringraum 16 des Zylinders 11, in dem eine Druckfeder 17 zwecks Rückstellung der Verstellvorrichtung 5 angeordnet ist, ist durch einen Leitungsabschnitt 18 mit der Verbindungsleitung 9 verbunden und somit mit dem Arbeitsdruck beaufschlagbar. Der soweit beschriebene Druckregler 6 einschließlich einer mit 19 bezeichneten, ggf, verstellbaren Düse in einer vom Kolbenraum 10 ausgehenden Ablaufleitung 20 und einer mit letzterer verbundenen, vom Regelventil 7 ausgehenden Parallelleitung 21, ist von üblicher Bauart und deshalb bekannt, so daß auf eine Funktionsbeschreibung im einzelnen verzichtet werden kann. Hervorzuheben ist, daß die Druckregler 6 einen Arbeitsdruck einstellen, der abgesehen von einer geringen Druckveränderung, im wesentlichen als konstant anzusehen ist. Die geringe Druckveränderung im Arbeitsdruck im Regelbereich des Druckreglers 6 ist durch die progressive Kennlinie der Federn 15 und 17, sowie durch Reibung und Eigenstellkräfte der Verstellvorrichtung 5 bedingt und beträgt bei üblichen Druckreglern 6 etwa 3 bar.Each adjusting device 5 of the pumps 1 is assigned a pressure regulator 6 with a first proportional control valve 7 in the form of a pressure compensator, the slide 8 of which regulates the passage of a connecting line 9 which starts from the associated working pressure line section 2 and into the piston chamber 10 of a cylinder 11 of the adjusting device 5 flows. For this purpose, the slide 8 is acted upon by a line section 12 with the working pressure against a valve spring 15, the spring force of which is optionally adjustable. The piston annular space 16 of the cylinder 11, in which a compression spring 17 is arranged for the purpose of resetting the adjusting device 5, is connected to the connecting line 9 by a line section 18 and can thus be subjected to the working pressure. The pressure regulator 6 described so far, including an adjustable nozzle, designated 19, in a discharge line 20 extending from the piston chamber 10 and a parallel line 21 connected to the latter and originating from the control valve 7 is of a conventional design and is therefore known, so that a functional description can be dispensed with in detail. It should be emphasized that the pressure regulators 6 set a working pressure which, apart from a slight change in pressure, can be regarded as essentially constant. The slight change in pressure in the working pressure in the control range of the pressure regulator 6 is due to the progressive characteristic curve of the springs 15 and 17, as well as to the friction and self-adjusting forces of the adjusting device 5, and is about 3 bar in the case of conventional pressure regulators 6.

Gemäß der Erfindung ist jeder Pumpe 1 ein allgemein mit 25 bezeichnetes Steuermittel zugeordnet, das ein noch zu beschreibendes zweites Regelventil 37 mit einem von der jeweiligen Fördermegeneinstellung der zugehörigen Pumpe 1 abhängigen Steuersignal sowie mit einem für alle Pumpen gemeinsamen Sollwertsignal beaufschlagt. Das Steuermittel 25 wird durch ein Druckbegrenzungsventil 26 gebildet, das in einer Leitung 27 angeordnet ist, die sich von Ausgang des Druckbegrenzungsventils 26 als Ablaufleitung 28 fortsetzt, und die hinter einer Drossel 29 von einer Leitung 30 abzweigt, die von der Arbeitsdruck enthaltenden Verbindungsleitung 9 ausgeht. Das Steuermittel 25 erzeugt im hinter der Drossel 29 beginnenden Abschnitt 31 der Leitung 30 ein von der jeweiligen Fördermengeneinstellung der zugehörigen Pumpe 1 abhängiges Steuersignal Xist. Zur Übertragung der der jeweiligen Fördermengeneinstellung entsprechenden Maßgabe dient ein Stellelement 32 in Form eines Stößels oder Taststiftes 33, der an seinem einen Ende eine am Verstellkolben 34 des Zylinders 11 außerhalb letzterem vorhandene Schrägfläche 35 anliegt und mittels einer Feder 36 auf den Schieber des Druckbegrenzungsventils 26 wirkt und gegen die Schrägfläche 35 beaufschlagt ist. Das Stellelement 32 ist in seiner Längsrichtung verschiebbar gelagert, so daß es bei einer Längsverstellung des Verstellkolbens 34 eine das Druckbegrenzungsventil verstellende Längsbewegung ausführt.According to the invention, each pump 1 is assigned a control means, generally designated 25, which acts on a second control valve 37 to be described with a control signal which is dependent on the respective delivery rate setting of the associated pump 1 and with a setpoint signal common to all pumps. The control means 25 is formed by a pressure relief valve 26, which is arranged in a line 27, which continues from the outlet of the pressure relief valve 26 as a discharge line 28, and which branches off behind a throttle 29 from a line 30 which starts from the connecting line 9 containing the working pressure . The control means 25 generates in the beginning after the restrictor 29 section 31 of the line 30 a depending on the particular delivery setting of the associated pump 1 control signal X is. An actuator 32 in the form of a plunger or stylus 33 is used to transmit the respective setting corresponding to the delivery quantity setting, which abuts at one end an inclined surface 35 present on the adjusting piston 34 of the cylinder 11 outside the latter and acts on the slide of the pressure relief valve 26 by means of a spring 36 and applied against the inclined surface 35 is. The adjusting element 32 is displaceably mounted in its longitudinal direction, so that when the adjusting piston 34 is adjusted longitudinally, it performs a longitudinal movement which adjusts the pressure limiting valve.

Zwischen den mit 47 und 48 bezeichneten Leitungen, die zum Regelventil 7 und zwar auf der dem Leitungsabschnitt 12 gegenüberliegenden Seite seines Schiebers 8 führt, ist das vorerwähnte zweite, mit 37 bezeichnete Regelventil (Proportional-Regelventil) in Form einer Druckwaage angeordnet, dessen Schieber 38 einerseits durch einen Leitungsabschnitt 39 mit der Leitung 30 und andererseits durch einen Leitungsabschnitt 41 mit einer Verbindungsleitung 42 verbunden ist, an die auch das der anderen Pumpe 1 zugehörige Regelventil 37 bzw. alle vorhandenen Regelventile 37 mittels der Leitungsabschnitte 41 angeschlossen sind. Die Leitung 30 und die Verbindungsleitung 42 sind im Bereich jedes Regelventils 37 durch eine letzteres umgehende Verbindungsleitung 43 kurzgeschlossen, in der eine Drossel 44 angeordnet ist. Die Drosseln 44 erzeugen in der Verbindungsleitung 42 ein Steuersignal Xsoll, das allen Regelventilen 37 gemeinsam ist. Am Regelventil 37, dessen Schieber 38 zu beiden Seiten mit einer Ventilfeder 45, 46 beaufschlagt ist, von denen die Federkraft der Ventilfeder 46 verstellbar ist, werden jeweils die Drucksignale Xist und Xsoll gegeneinander abgewogen, wodurch das Regelventil 37 in der Leitung 47 ein Korrektursignal XK erzeugt, welches am Regelventil 7 eine Regelabweichung Xist-Xsoll signalisiert. Die Leitung 48 kann extern mit einem beliebigen Druck belastet werden oder vereinfacht am Knotenpunkt 49 mit dem Leitungsabschnitt 31 verbunden werden. Ebenso wäre eine Verbindung der Leitung 48 mit der Leitung 9 möglich, ähnlich der noch zu beschreibenden Ausführung in Fig. 3.Between the lines labeled 47 and 48, which leads to the control valve 7, namely on the side of its slide 8 opposite the line section 12, the aforementioned second control valve (proportional control valve), designated 37, is arranged in the form of a pressure compensator, the slide 38 of which is connected on the one hand by a line section 39 to the line 30 and on the other hand by a line section 41 to a connecting line 42, to which the control valve 37 associated with the other pump 1 or all the existing control valves 37 are also connected by means of the line sections 41. The line 30 and the connecting line 42 are short-circuited in the region of each control valve 37 by a connecting line 43 which circumvents the latter and in which a throttle 44 is arranged. The throttles 44 generate a control signal X soll in the connecting line 42, which is common to all the control valves 37. On the control valve 37, the slide 38 of which is acted upon on both sides by a valve spring 45, 46, of which the spring force of the valve spring 46 is adjustable, the pressure signals X is and X is to be weighed against one another, as a result of which the control valve 37 is in line 47 correction signal X K generated, which the control valve 7 is a control deviation X is -X is to be signaled. The line 48 can be loaded externally with any pressure or, in a simplified manner, be connected to the line section 31 at the node 49. A connection of line 48 to line 9 would also be possible, similar to the embodiment to be described in FIG. 3.

Die Anordnung ist so getroffen, daß das Druckbegrenzungsventil 26 beim Einschwenken der Verstellvorrichtung 5, d.h. bei einer Verstellbewegung des Verstellkolbens 34 nach links, öffnet, wodurch das Steuersignal Xist bzw. der in der Verbindungsleitung 31 vorhandene Steuerdruck verringert wird, d.h. es wird ein bei dieser Verstellbewegung degressives Drucksignal Xist und mittels des Regelventils 37 ein progressives Drucksignal Xm erzeugt. Letzteres beaufschlagt den Schieber 8 des Regelventils 7 entgegen dem Arbeitsdruck. Damit steht der Arbeitsdruck am Regelventil 7 nicht mehr nur zu der Kraft der Feder 15 (Reglereinstellung) im Gleichgewicht, sondern die Reglereinstellung erhöht sich in Abhängigkeit der Regelabweichung Xist-Xsoll um das Drucksignal XK. Es ergibt sich somit bei unterschiedlicher Fördermenge bzw. Schwenkstellung eine Druckerhöhung in der Reglereinstellung an der Pumpe mit der geringeren Fördermenge, wodurch diese Pumpe veranlaßt wird, weiter auszuschwenken bis die Drucksignal Xist und Xsoll gleich groß sind und sich die Druckerhöhung wieder aufbaut.The arrangement is such that the pressure relief valve 26 opens when the adjusting device 5 is pivoted in, ie during an adjusting movement of the adjusting piston 34 to the left, as a result of which the control signal X is or the control pressure present in the connecting line 31 is reduced, ie it becomes a this adjustment is degressive pressure signal X and generated by means of the control valve 37 a progressive pressure signal X m. The latter acts on the slide 8 of the control valve 7 against the working pressure. Thus, the working pressure at the control valve 7 is no longer only in equilibrium with the force of the spring 15 (controller setting), but the controller setting increases as a function of the control deviation X ist -X soll by the pressure signal X K. There is thus at a different flow rate or pivot position, a pressure increase in the controller setting on the pump with the lower flow rate, thereby causing said pump to continue to swing out until the pressure signal X, and X should have the same size and the increase in pressure builds up again.

Aufgrund dieser Sachverhalte ist die Gesamtfördermengeneinstellung der Pumpen 1 von dem auf die Druckregler 6 wirkenden im wesentlichen gleich großen Arbeitsdruck bestimmt.On the basis of these facts, the total delivery rate setting of the pumps 1 is determined by the essentially equal working pressure acting on the pressure regulator 6.

Die angestrebte gleichmäßige Aufteilung der Fördermenge auf die Pumpen 1 ist von der Abweichung der jeweiligen Drucksignal Xist vom gemeinsamen gemittelten Drucksignal Xsoll und der daraus resultierenden Beeinflussung der Regelventile 7 durch das Korrektursignal XK bestimmt.The desired even distribution of flow to the pump 1 is of the deviation of the respective pressure signal X to the common average pressure signal X and the resulting impact on the control valves 7 determined by the correction signal X K.

Da sich die Druckerhöhung am Regelventil 7 einer evtl. weniger fördernden Pumpe nach dem Ausregeln auf gleiche Fördermenge wieder abbaut, wird der angestrebte Gleichlauf ohne bleibenden Druckanstieg in der Reglerkennlinie erreicht.Since the pressure increase at the control valve 7 of a possibly less pumping pump decreases again after the regulation to the same delivery rate, the desired synchronism becomes achieved without permanent pressure increase in the controller characteristic.

Die erfindungsgemäße Ausgestaltung eignet sich für in beide Förderrichtungen einstellbare Pumpen. In diesem Fall ist es vorteilhaft, die Anordnung so zu treffen, daß in der Nullstellung der Pumpen das Stellelement 32 sich in mittlerer Stellung zur Länge der Schrägfläche 35 befindet.The configuration according to the invention is suitable for pumps which can be set in both delivery directions. In this case, it is advantageous to make the arrangement so that when the pumps are in the zero position, the actuating element 32 is in the middle position relative to the length of the inclined surface 35.

Beim Ausführungsbeispiel gemäß Fig. 2 sind die ersten Regelventile 7 mit einem gemeinsamen Fernsteuerventil 52 verbunden, das durch ein Druckbegrenzungsventil gebildet sein kann. Beim gezeigten Ausführungsbeispiel werden die zweiten Regelventile 51 durch verstellbare Drosseln 53 gebildet, die jeweils in Leitungsabschnitten 54 angeordnet sind, die von das Steuersignal XK haltenden Leitungsabschnitten 55 ausgehen und zu einer gemeinsamen, an den Ablauf angeschlossenen Verbindungsleitung 56 führen, in der das Fernsteuerventil 52 angeordnet ist. Ein wesentlicher Unterschied zum ersten Ausführungsbeispiel besteht darin, daß die das Steuersignal XK enthaltenden Leitungsabschnitte 55 über Leitungsabschnitte 57 mit Drosseln 58 direkt an die den Arbeitsdruck enthaltenden Verbindungsleitung 9 angeschlossen sind. Wie schon beim Ausführungsbeispiel gemäß Fig. 1 ist auch beim Ausführungsbeispiel gemäß Fig. 2 eine das Regelventil 51 umgehende Verbindungsleitung 59 mit einer Drossel 60 vorhanden, an die die das Drucksignal Xist und die das Drucksignal Xsoll enthaltenden Leitungen 31, 42 angeschlossen sind, wobei der Schieber des Regelventils 51 durch mit dem Ausführungsbeispiel gemäß Fig. 1 vergleichbare Leitungsabschnitte 61, 62 einerseits mit dem Drucksignal Xist und andererseits mit dem Drucksignal Xsoll gleichzeitig beaufschlagbar ist. Es sind auch bei diesem Ausführungsbeispiel zu beiden Seiten des Schiebers Ventilfedern 63, 64 vorhanden, von denen die Ventilfeder 64 verstellbar ist.In the exemplary embodiment according to FIG. 2, the first control valves 7 are connected to a common remote control valve 52, which can be formed by a pressure limiting valve. In the exemplary embodiment shown, the second control valves 51 are formed by adjustable throttles 53, which are each arranged in line sections 54, which originate from line sections 55 holding the control signal X K and lead to a common connecting line 56 connected to the outlet, in which the remote control valve 52 is arranged. An essential difference from the first exemplary embodiment is that the line sections 55 containing the control signal X K are connected directly to the connecting line 9 containing the working pressure via line sections 57 with throttles 58. As with the embodiment of FIG. 1 is a control valve 51 immediate connection line 59 provided with a throttle 60, to which is the pressure signal X and to the pressure signal X containing lines 31 are connected 42 also in the embodiment of Fig. 2, wherein the slide of the control valve 51 by comparable with the embodiment according to FIG. 1 line sections 61, 62 on the one hand is connected to the pressure signal X, and on the other hand to the pressure signal X is simultaneously acted upon. They are too In this embodiment, valve springs 63, 64 are provided on both sides of the slide, of which the valve spring 64 is adjustable.

Auch beim Ausführungsbeispiel gemäß Fig. 2 öffnet das Druckbegrenzungsventil 26. beim Einschwenken der Verstellvorrichung 5 um einen gewissen Betrag, wodurch das Drucksignal Xist durch Druckentlastung im Leitungsabschnitt 31 erzeugt wird. Aufgrund der Druckentlastung wird der Schieber des Regelventils 51 geringfügig nach links verschoben, wodurch der Durchgang im Regelventil 51 gedrosselt wird und im Leitungsabschnitt 55 ein sich vergrößernder Druck aufgebaut wird, der die Kraft der Ventilfeder 15 unterstützend den Schieber 8 des Regelventils 6 progressiv beaufschlagt, wodurch die Druckerhöhung in der Reglerkennlinie erreicht wird. Es ergibt sich somit auch bei diesem Ausführungsbeispiel bei unterschiedlicher Fördermenge bzw. Schwenkstellung eine Druckerhöhung in der Reglereinstellung an der Pumpe mit der geringeren Fördermenge, wodurch diese Pumpe veranlaßt wird, weiter auszuschwenken bis die Drucksignal Xist und Xsoll gleich groß sind und sich die Druckerhöhung wieder aufbaut.Also in the exemplary embodiment according to FIG. 2, the pressure limiting valve 26 opens when the adjusting device 5 is pivoted in by a certain amount, as a result of which the pressure signal X ist is generated by pressure relief in the line section 31. Due to the pressure relief, the slide of the control valve 51 is shifted slightly to the left, as a result of which the passage in the control valve 51 is throttled and an increasing pressure is built up in the line section 55, which progressively acts on the slide 8 of the control valve 6 to support the force of the valve spring 15, as a result of which the pressure increase in the controller characteristic is reached. Thus, there is also in this embodiment, with different delivery or pivot position, a pressure increase in the controller setting on the pump with the lower flow rate, whereby this pump is caused to continue to swing out until the pressure signal X, and X should have the same size and the pressure increase rebuilds.

Aufgrund dieser Sachverhalte ist die Gesamtfördermengeneinstellung der Pumpen 1 von dem auf die Druckregler 6 wirkenden im wesentlichen gleich großen Arbeitsdruck bestimmt.On the basis of these facts, the total delivery rate setting of the pumps 1 is determined by the essentially equal working pressure acting on the pressure regulator 6.

Die angestrebte gleichmäßige Aufteilung der Fördermenge auf die Pumpen 1 ist von der Abweichung der jeweiligen Drucksignal Xist vom gemeinsamen gemittelten Drucksignal Xsoll und der daraus resultierenden Beeinflussung der Regelventile 7 durch das Korrektursignal XK bestimmt.The desired even distribution of flow to the pump 1 is of the deviation of the respective pressure signal X to the common average pressure signal X and the resulting impact on the control valves 7 determined by the correction signal X K.

Da sich die Druckerhöhung am Regelventil 7 einer evtl. weniger fördernden Pumpe nach dem Ausregeln auf gleiche Fördermenge wieder abbaut, wird der angestrebte Gleichlauf ohne bleibenden Druckanstieg in der Reglerkennlinie erreicht.Since the pressure increase at control valve 7 If the pump that pumps less of the pump is reduced to the same delivery rate again after adjustment, the desired synchronism is achieved without a permanent pressure increase in the controller characteristic curve.

Mit Hilfe des Fernsteuerventils 52 können gleichzeitig die bzw. alle Regelventile 7 bzw. Druckregler 6 gleichzeitig mit nur einem Steuerglied gesteuert werden.With the help of the remote control valve 52, the or all control valves 7 or pressure regulator 6 can be controlled simultaneously with only one control element.

Beim Ausführungsbeispiel gemäß Fig. 3, bei dem gleiche Teile mit gleichen Bezugszeichen versehen sind, ist jeweils in der die Arbeitsdruckleitung mit dem Kolbenraum 10 des Zylinders 11 der Verstelleinrichtung 5 verbindenden Verbindungsleitung 9 ein Regelventil 71 angeordnet, dessen Schieber 72 einerseits mit dem vom Druckbegrenzungsventil 26 eingestellten Drucksignal Xist und andererseits mit dem gemittelten Drucksignal Xsoll beaufschlagbar ist, und das prinzipiell dem zweiten Regelventil 37 gemäß Fig. 1 entspricht. Auch hier ist die das Regelventil 71 umgehende Verbindungsleitung 43 mit der Drossel 44 vorhanden, die einerseits an die das Drucksignal Xsoll enthaltende Verbindungsleitung 42 und andererseits über die Drossel 29 an die den Arbeitsdruck enthaltende Verbindungsleitung 9 angeschlossen ist. Auch der Schieber 72 des Regelventils 71 ist beiderseits durch die Kräfte von Ventilfedern 73, 74 beaufschlagt, wobei die Kraft der Ventilfeder 74 einstellbar ist.In the exemplary embodiment according to FIG. 3, in which the same parts are provided with the same reference numerals, a control valve 71 is arranged in the connecting line 9 connecting the working pressure line to the piston chamber 10 of the cylinder 11 of the adjusting device 5, the slide 72 of which, on the one hand, is connected to that of the pressure relief valve 26 set pressure signal X, and on the other hand to the averaged pressure signal X can be acted upon, and that in principle corresponds to 37 in FIG. 1 the second control valve. Again, the control valve 71 immediate connection line 43 is provided with the restrictor 44, on the one hand to the pressure signal X should compound containing line 42, and on the other hand connected to the containing the working pressure connection pipe 9 via the restrictor 29th The slide 72 of the control valve 71 is also acted upon on both sides by the forces of valve springs 73, 74, the force of the valve spring 74 being adjustable.

Ein wesentlicher Unterschied zu den Ausführungsbeispielen gemäß Fig. 1 und 2 besteht darin, daß ein für die bzw. alle Pumpen 1 gemeinsames Regelventil 76 vorgesehen ist, das in einer von der Arbeitsdruckleitung 3 abzweigenden Leitung 77 angeordnet ist, von der zu jeder Verstellvorrichtung 5 ein Leitungsabschnitt 78 mit einer Drossel 79 abzweigt, der zwischen dem Regelventil 71 und dem Kolbenraum 10 der Verstellvorrichtung 5 an die Verbindungsleitung 9 angeschlossen ist. Das Regelventil 76 regelt dadurch den Druck im Kolbenraum 10 aller Pumpen und somit die Verstellvorrichtung 5 aller Pumpen gleichzeitig. Auch bei diesem Ausführungsbeispiel wird am Regelventil 71 das Drucksignal Xist gegen das gemittelte Drucksignal Xsoll abgewogen und der Ventilschieber 72 nimmt eine von der Regelabweichung Xist-Xsoll abhängige Position ein. Hierdurch wird der Druck hinter der Drossel 79 (also im Leitungsabschnitt 81 bzw. im Kolbenraum 10) je nach Regelabweichung erhöht oder entlastet bis die Regelabweichung Xist-Xsoll ausgeglichen ist und alle Pumpen die gleiche Schwenkstellung einnehmen. Das Regelventil 76, das beim vorliegenden Ausführungsbeispiel ein Druckregelventil ist, wird durch den mit der Arbeitsdruckleitung 3 verbundenen Leitungsabschnitt 82 gegen eine Ventilfeder 83 mit Arbeitsdruck beaufschlagt.An essential difference from the exemplary embodiments according to FIGS. 1 and 2 is that a control valve 76 which is common to all pumps 1 is provided and which is arranged in a line 77 branching off from the working pressure line 3, from which to each adjusting device 5 Line section 78 branches off with a throttle 79, which is between the control valve 71 and Piston chamber 10 of the adjusting device 5 is connected to the connecting line 9. The control valve 76 thereby regulates the pressure in the piston chamber 10 of all pumps and thus the adjustment device 5 of all pumps simultaneously. In this exemplary embodiment, too, the pressure signal X ist is weighed against the averaged pressure signal X soll at the control valve 71 and the valve slide 72 assumes a position dependent on the control deviation X ist -X soll . As a result, the pressure behind the throttle 79 (that is to say in the line section 81 or in the piston chamber 10) is increased or relieved, depending on the control deviation, until the control deviation X is -X should be equalized and all pumps assume the same swivel position. The control valve 76, which is a pressure control valve in the present exemplary embodiment, is acted upon by the line section 82 connected to the working pressure line 3 against a valve spring 83 with working pressure.

Bei den vorbeschriebenen Ausführungsbeispielen sind die Regelventile 37, 51 und 71 aufgrund der beiderseitigen Beaufschlagung von Ventilfedern mittenzentriert. Sie sind somit in der Lage, einerseits und/oder andererseits wirksame Drucksignale zu verarbeiten, was je nach Größe der vorhandenen Regelabweichung Xist-Xsoll erfolgt.In the exemplary embodiments described above, the control valves 37, 51 and 71 are centered on the center due to the action of valve springs on both sides. They are thus able on the one hand and / or on the other hand to process signals effective pressure, which is depending on the size of the existing control deviation X -X should effected.

Aus Vereinfachungsgründen ist lediglich beim Ausführungsbeispiel gemäß Fig. 3 schematisch der Durchgang bzw. die Leitungsverbindung in der Mittelstellung angedeutet. Hier ist dem Regelventil 71 sowohl eingangsseitig als auch ausgangsseitig zum Ablauf hin jeweils eine Drossel 84 bzw. 85 zugeordnet.For reasons of simplification, only in the exemplary embodiment according to FIG. 3 the passage or the line connection is indicated schematically in the middle position. In this case, a throttle 84 or 85 is assigned to the control valve 71 both on the input side and on the output side toward the outlet.

Fig. 4 zeigt als Ausführungsbeispiel eine Schnittansicht eines Druckbegrenzungsventils 26 in vergrößerter Darstellung. Das Stellelement 32 wirkt mittels der einerseits an ihr abgestützen und andererseits am Schieber 87 angreifenden Feder 88 auf den Schieber 87 des Druckbegrenzungsventils 26, der mittels Steuerkanten 89 des Steuersignals Xist, d.h. den den Schieber 87 beaufschlagenden Steuerdruck einregelt. Hierbei geben die Steuerkanten 89 zwischen dem Schieber 87 und der ihn aufnehmenden Bohrung 91 den Ab- bzw. Rücklauf durch den Kanal 92 im Ventilgehäuse 93 mehr oder weniger frei.4 shows, as an exemplary embodiment, a sectional view of a pressure limiting valve 26 in an enlarged view. The actuating element 32 acts on the one hand her abgestützen and on the other hand engaging on the slide 87 spring 88 on the slider 87 of the pressure relief valve 26, which is the control signal X by means of control edges 89 that is, the slider 87 regulates acting control pressure. Here, the control edges 89 between the slide 87 and the bore 91 receiving it release or drain through the channel 92 in the valve housing 93 more or less.

Das Ventilgehäuse 93 ist im Gehäuse des Zylinders 11 bzw. einem Anbauteil desselben eingeschraubt. Der Schieber 87 befindet sich in einer Einstellbuchse 94, die mittels einem Gewinde 95 durch Drehen an einem Angriffselement, hier einem Innensechskant 96, axial im Ventilgehäuse 93 verstellbar und mittels einer auf der Einstellbuchse 94 aufgeschraubten Kontermutter 97 feststellbar ist. Zwischen dem Anschluß 98, der z.B. gemäß Fig. 1 und 2 an die Leitung 27 anschließbar ist, und einer die Bohrung 91 in der Einstellbuchse 94 schneidenden Querbohrung 99 die der Leitung 27 entspricht, ist eine Eingangsdrossel 100 angeordnet, die den Drosseln 29 entspricht.The valve housing 93 is screwed into the housing of the cylinder 11 or an attachment part of the same. The slide 87 is located in an adjusting bush 94, which can be adjusted axially in the valve housing 93 by means of a thread 95 by turning an attack element, here a hexagon socket 96, and can be locked by means of a lock nut 97 screwed onto the adjusting bush 94. Between port 98, e.g. 1 and 2 can be connected to the line 27, and a transverse bore 99 which intersects the bore 91 in the adjusting bush 94 and which corresponds to the line 27, an input throttle 100 is arranged which corresponds to the throttles 29.

An den Anschluß 101 ist die Leitung 31 anschließbar.The line 31 can be connected to the connection 101.

Claims (8)

  1. A regulating device for at least two hydrostatic machines that have variable displacement or intake volumes and are linked to a common pressure line, wherein each machine has associated with it an adjusting device having a hydraulic adjusting piston and a regulator for regulating its volume setting, characterised in that each regulator (6) has associated with it control means (25, 59, 71) that applies to the associated regulator (6) a correction signal (XK) that is generated in dependence on a control signal (Xist [Xactual]) that depends substantially linearly on the volume setting of the associated machine (1) and an intended value (Xsoll [Xintended]) which is a preferably hydraulic mean value of the control signals (Xist (Xactual]) of all the machines (1).
  2. A regulating device according to claim 1, characterised in that the control means is controllable by a position sensor that cooperates with the adjusting device (5) or an extension thereof.
  3. A regulating device according to claim 2, characterised in that the position sensor comprises an oblique face (35) on a part of the adjusting device (5), preferably on the adjusting piston (34), and an adjusting element (32) that senses the oblique face (35).
  4. A regulating device according to any one of claims 1 to 3, characterised in that the control means has an adjustable throttle or a pressure regulating valve, in particular a pressure limiting valve (26).
  5. A regulating device according to any one of claims 2 to 4, characterised in that the machines (1) are arranged for operation in both directions and the position sensor is in its zero position when the adjusting devices are in their central position.
  6. A regulating device according to any one of claims 1 to 5, characterised in that a regulating valve (7) in the form of a pressure balance to which on one side the working pressure can be applied against a valve spring (15) and the correction signal (XK) can be applied on the other side.
  7. A regulating device according to any one of claims 1 to 6, characterised in that the control means includes a second regulating valve (37; 51; 71) in the form of a pressure balance which can be subjected on one side to the control signal (Xist [Xactual]) dependent on the volume setting of the associated machine (1) and on the other side to the mean value (Xsoll [Xintended]) of the control signal (Xist [Xactual]).
  8. A regulating device according to any one of claims 1 to 7, characterised in that each regulator (6) is connected through branch lines (54) to a common remote control valve (52).
EP88104660A 1987-04-02 1988-03-23 Regulator for at least two hydrostatic machines linked to a common pressure pipe Expired - Lifetime EP0284987B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3711050 1987-04-02
DE19873711050 DE3711050A1 (en) 1987-04-02 1987-04-02 CONTROL DEVICE FOR AT LEAST TWO HYDROSTATIC MACHINES CONNECTED TO A COMMON WORKING PRESSURE LINE

Publications (3)

Publication Number Publication Date
EP0284987A2 EP0284987A2 (en) 1988-10-05
EP0284987A3 EP0284987A3 (en) 1989-12-27
EP0284987B1 true EP0284987B1 (en) 1991-09-18

Family

ID=6324676

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88104660A Expired - Lifetime EP0284987B1 (en) 1987-04-02 1988-03-23 Regulator for at least two hydrostatic machines linked to a common pressure pipe

Country Status (2)

Country Link
EP (1) EP0284987B1 (en)
DE (2) DE3711050A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4025638C1 (en) * 1990-08-13 1991-12-05 Brueninghaus Hydraulik Gmbh, 7240 Horb, De
DE19601544C1 (en) * 1996-01-17 1997-07-24 Hydrokraft Gmbh Flow controller
DE19626793C1 (en) * 1996-07-03 1997-06-26 Brueninghaus Hydromatik Gmbh Hydraulic equipment for parallel regulation of hydrostatic displacement pumps

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1188948B (en) * 1960-07-16 1965-03-11 Metallwerk Glockerau G M B H Working fluid quantity control device for hydrostatic pumps and motors
GB1056655A (en) * 1964-11-16 1967-01-25 Ifield & Sons Pty Ltd R J Torque control means for variable displacement hydraulic pumps
DE2017656A1 (en) * 1969-04-23 1970-11-05 Pensa, Carlo, Esino Lario, Como (Italien) Hydraulic flow rate adjustment device for one or more pumps
US4055046A (en) * 1976-12-22 1977-10-25 Caterpillar Tractor Co. Control system having override for fluid operated work elements
CA1104033A (en) * 1977-02-24 1981-06-30 Commercial Shearing, Inc. Pressure and flow compensated control system with constant torque and viscosity sensing over-ride
DE3345264A1 (en) * 1983-12-14 1985-06-27 Brueninghaus Hydraulik Gmbh, 7240 Horb TORQUE CONTROL UNIT FOR AN ADJUSTABLE HYDROPUMP

Also Published As

Publication number Publication date
DE3711050A1 (en) 1988-10-20
EP0284987A2 (en) 1988-10-05
DE3711050C2 (en) 1992-02-13
EP0284987A3 (en) 1989-12-27
DE3864867D1 (en) 1991-10-24

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