EP0397840B1 - Hydraulic circuit - Google Patents

Hydraulic circuit Download PDF

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Publication number
EP0397840B1
EP0397840B1 EP90900115A EP90900115A EP0397840B1 EP 0397840 B1 EP0397840 B1 EP 0397840B1 EP 90900115 A EP90900115 A EP 90900115A EP 90900115 A EP90900115 A EP 90900115A EP 0397840 B1 EP0397840 B1 EP 0397840B1
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EP
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Prior art keywords
flow
hydraulic
bore
partial flows
diaphragm arrangement
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EP90900115A
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German (de)
French (fr)
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EP0397840A1 (en
Inventor
Walter Krumrey
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Bucher GmbH Maschinenfabrik
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Bucher GmbH Maschinenfabrik
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/022—Flow-dividers; Priority valves

Definitions

  • the invention relates to a hydraulic circuit arrangement known from DE-A-2751082 and of the generic type with a pressure medium source for supplying a hydro stream, two consumers driven by partial streams of the hydro stream and a proportional flow dividing valve through which the hydro stream and the two partial streams flow, the division ratio between the two orifice arrangement determining the two partial flows is provided with a first actuating device which serves to specify the division ratio.
  • the two consumers can be supplied by the hydraulic current supplied by a single pump which forms the pressure medium source.
  • a single pump which forms the pressure medium source.
  • this allows the relative flow volume of the two partial flows to be adjusted in relation to one another, the total flow volume and thus also the flow volume of the partial flows are subject to fluctuations, since the hydraulic flow supplied by the hydraulic pump is normally not constant. Furthermore, even with a constant total flow rate of the hydro stream, the flow rate of the two partial flows cannot be controlled.
  • the invention is based on the object, a hydraulic circuit arrangement of the type mentioned to further develop that the flow quantity can be set in the case of two consumers supplied with partial flows of an adjustable division ratio from a single pressure medium source.
  • this object is achieved in that the orifice arrangement is provided with a second actuating device for specifying its total passage cross section, and the pressure medium source has a regulating device for load-dependent control of the hydroflow it supplies, to the control input of which a control signal corresponding to the pressure difference between the pressures on both sides of the orifice arrangement is applied is.
  • Pressure medium sources the hydroflow of which is regulated depending on the load, are known, for example, under the name LS pumps (load-sensing pumps).
  • the control signal required to regulate the total flow rate of the hydraulic current supplied by the pressure medium source is obtained in a particularly simple manner in the invention by setting the total passage cross section of the orifice arrangement to a desired predetermined value fixed with the second adjusting device.
  • the pressure difference occurring with a predetermined setting of the orifice arrangement can thus easily be detected without additional circuit parts and used as the control signal required to control the control device. This means that the two consumers can be supplied with partial flows with a low level of structural complexity, in which not only the division ratio but also the flow rate are set to the desired values.
  • a configuration of the proportional flow divider valve which is particularly expedient for the hydraulic circuit arrangement consists in the fact that the orifice arrangement has an outer hollow body and an inner hollow body sealingly mounted therein, which is acted upon by the hydraulic flow in its interior and which are each provided with two radial passages through which the two partial flows flow, whose axial overlap determining the total passage cross section can be adjusted by means of the second adjusting device by a mutual axial displacement of the two cabbage bodies and whose azimuthal overlap determining the division ratio can be adjusted by means of the first adjusting device by mutual rotation of the two hollow bodies.
  • the setting of the total flow rate and the division ratio between the two partial flows is determined by the degree of overlap of the radial passages provided in the two hollow bodies certainly.
  • the radial passages are arranged relative to one another in such a way that, in the event of a mutual rotation caused by the first adjusting device, the common clear opening of the one overlapping pair of radial passages decreases as the common clear opening of the other pair of radial passages increases, as a result of which the division ratio of the hydroflow passing through the radial passages into its two partial flows is determined.
  • the mutual axial displacement of the two hollow bodies by means of the second adjusting device brings about a change in the same direction of the clear opening of the overlapping pairs of radial passages, so that the total flow rate is thereby set.
  • a pressure compensator which is acted upon by the pressure of the two partial flows on the control side, is connected between the orifice arrangement and the two consumers. Since the two consumers are connected to the proportional flow divider valve via the pressure compensator, they are regulated independently of the load.
  • the pressure compensator has two hollow pistons which are arranged so as to be axially displaceable in a mirror-inverted manner in a bore in a housing block and are provided with two axially spaced radial passage regions and which, on their mutually facing, closed, pressurized by the pressure of the hydraulic flow End faces are provided with mutually interlocking stop parts that limit their axial relative position between an extended position and a pushed-together position, and that each has a passage area of each hollow piston one of the partial flows of the orifice arrangement communicates and the other passage region interacts with a radial annular space in the bore of the housing block which is connected to the respective consumer and serves as a control edge.
  • the housing block it finally proves to be expedient for the housing block to have a further bore which radially penetrates the bore in the region between the two hollow pistons of the pressure compensator and whose open end on one side of the bore receiving the hollow pistons of the pressure compensator forms a connection for the hydroflow and in which on the other side of the section located the bore receiving the cabbage pistons of the pressure compensator is arranged the diaphragm arrangement.
  • an LS pump (load-sensing pump) 1 is used to deliver a load-dependent controlled hydro stream from a hydraulic tank 2.
  • Two consumers 5, 5 ' are connected to the LS pump 1 via a 4/3 way valve 3 and a proportional flow divider valve 4, which are, for example, hydraulic drive motors of a travel drive or hydraulic drives of various types of working machines can.
  • the proportional flow divider valve 4 has an orifice arrangement 6, shown schematically in FIG. 1, on which the branching takes place between the hydroflow of the LS pump 1 occurring at a connection 7 and the two partial flows of the hydroflow occurring at connections 8, 9.
  • a first actuating device 10 which can be formed, for example, by a magnetic actuator, serves to set the division ratio of the two partial flows occurring at the ports 8 and 9 at the orifice arrangement 6.
  • a second actuating device 11 which can also be formed by a magnetic actuator, acts on the diaphragm arrangement 6 in order to set the overall passage cross section of the diaphragm arrangement 6 to a desired, predetermined value.
  • a pressure compensator 12 is connected between the connections 8, 9 and the orifice arrangement 6 and is acted upon on the control side by the pressures of the two partial flows occurring at the orifice arrangement 6.
  • the control device of the LS pump 1 which is of a known type and therefore not shown in detail, has a control input 13 with two connections 14, 15, to which a control signal corresponding to a pressure difference is to be applied in such a way that the connection 14 in each case has the higher pressure value and port 15 receives the lower pressure value.
  • the pressure difference that occurs at the orifice arrangement 6 and the control lines 16, 17 serves as the pressure difference 14, 15 is fed.
  • the hydraulic circuit arrangement operates normally, in which the LS pump 1 promotes its hydroflow to the connection 7 of the proportional flow divider valve 4 , which divides the hydraulic flow according to the setting specified by the first adjusting device 10 into the two partial flows that are in a certain relationship to one another and by means of the control edges of the pressure compensator 12 supplies the consumers 5, 5 'in a controlled manner, from where the two partial flows via a common one Tile line 18 and the 4/3 way valve 3 back to the hydraulic tank 2.
  • a parallel connection of two shuttle valves 19, 20 is connected between the two sides of the orifice arrangement 6.
  • the shuttle valve 19 is constructed in such a way that it connects the higher pressure value to the control line 16 Connection 21 switches through, while the shuttle valve 20 switches through the respectively lower pressure value to a connection 22 to which the control line 17 is connected. This ensures that the control signal is properly switched through to the control input of the LS pump 1 in both operating modes, namely normal operation and reversing operation.
  • FIG. 2 shows an embodiment of the proportional flow divider valve 4 intended for the hydraulic circuit, in which the orifice arrangement 6 and the pressure compensator 12 are assembled in a common housing block 23.
  • the housing block 23 has a bore 24 extending horizontally with its axis in the illustration in FIG. 2 and a further bore 25 crossing the bore 24 perpendicularly in the middle of its axial length.
  • an outer hollow body 26 of the diaphragm arrangement 6 is axially immovable, but is rotatable about the axis in the azimuthal direction by a certain angular amount. This angular rotation of the hollow body 26 takes place in the exemplary embodiment of FIG.
  • an inner hollow body 28 is sealingly supported, which is supported in a rotationally fixed manner in the housing block 23 by a radial cam 30 guided in a longitudinal groove 29 of the housing block 23.
  • a closing part which closes the upper end of the further bore 25 in FIG. 2 and has an axially adjustable actuator 31 serves as the second adjusting device 11.
  • the outer and the inner hollow body 26 and 28 are each provided with two radial passages 33, 33 'and 34, 34', the mutual overlap of which is set in the axial direction by the actuator 31 and in the azimuthal direction by the worm spindle 27.
  • the clear passage opening determined by the overlap of the radial passages 33, 34 is reduced to the same extent as the clear passage opening determined by the overlap of the radial passages 33 ', 34'.
  • the total passage cross section is determined by the total passage cross section determined by the lobes of the radial passages 33, 34 and 33 ', 34'.
  • the hydraulic flow generated by the LS pump 1 thus flows through the open end of the further bore 25 forming the connection 7 of FIG. 1, which is opposite the closed end provided with the actuator 31, into the interior of the inner hollow body 28 enters and passes through the radial passages 33, 34 and 33 ', 34'.
  • the partial flows of the hydraulic flow which are set with regard to the total flow quantity and the division ratio are thus available on channels 35, 35 'of the housing block 23 which communicate with the radial passages 33, 33' of the outer hollow body 26.
  • each hollow piston 37, 37 ' has two radial passage regions 38, 39 and 38', 39 ', axially spaced apart from one another, of which the radial passage regions 38 and 38', which are further away from the locking screws 36, 36 ', with those into the bore 24 opening channels 35 and 35 'communicate.
  • the radial passage regions 39, 39 ' which are respectively closer to the locking screws 36, 36', cooperate with radial annular spaces 40 and 40 'in the bore 24, these radial annular spaces 40, 40' via inner channels 41, 41 'with those in FIGS the outer connections 8 and 9 provided to the housing block 23 are connected.
  • the axial position of the radial passage areas 39, 39 'with respect to the radial annular spaces 40 and 40' is selected such that the boundary edges of the annular spaces 40 and 40 'act as control edges with the radial passage areas 39, 39' as soon as the Cabbage pistons 37, 37 'are displaced from their central position symmetrical to the axis of the further bore 25 under the influence of the pressure conditions.
  • all radial passage areas 38, 38 ', 39, 39' are each formed by a certain number of holes which are distributed around the circumference of the hollow pistons 37, 37 'at the same angular distance.
  • the hollow pistons 37, 37 ' are each provided with hook-shaped stop parts 42, 42' which, when the two hollow pistons 37, 37 'are in a maximally extended position, abut one another and thereby limit a further separating movement of the hollow pistons 37, 37' .
  • the stop part 42 of the hollow piston 37 is supported on the end face of the other hollow piston 37 'in a maximally pushed-together position, and vice versa, so that even in the maximally pushed-together position of the two hollow pistons 37, 37 'there is still a clear passage between their mutually facing end faces.
  • the LS pump 1 promotes the hydraulic flow in the direction of arrow 43 through the channel left between the two hollow pistons 37, 37 'of the pressure compensator 12 in the further bore 25 to the interior of the inner hollow body 28 of the orifice arrangement 6, as a result of which the move the two hollow pistons 37, 37 'into their extended positions.
  • the partial flows of the hydroflow occurring at the orifice arrangement 6 are supplied to the annular spaces 40 and 40 'via the channels 35 and 35', the radial passage areas 38 and 38 'and the radial passages 39 and 39' and are formed by the latter Control edges are kept constant regardless of load and fed to connections 8 and 9.

Abstract

In a hydraulic circuit for supplying two consumers (5, 5') from a single hydraulic medium source through a proportional flow distributing valve (4) which splits the total flow into two partial flows, the diaphragm arrangement (6) which splits the hydraulic flow is provided with an additional regulating device (11) which predetermines the total through-flow cross-section. The pressure differential signal produced at the diaphragm arrangement (6) in function of the setting of the total through-flow cross-section is fed, in an appropriate manner for both directions of through-flow, to the control connections (13) of the hydraulic medium source in the form of a load-sensing pump (1), by means of a shuttle valve arrangement (19, 20). As a result, a predetermined volume of fluid is delivered to the consumers (5, 5').

Description

Die Erfindung bezieht sich auf eine aus der DE-A-2751082 bekannte und gattungsgemäße hydraulische Schaltungsanordnung mit einer Druckmittelquelle zur Lieferung eines Hydrostroms, zwei von Teilströmen des Hydrostroms angetriebenen Verbrauchern und einem von dem Hydrostrom und den beiden Teilströmen durchströmten Proportionalstromteilerventil, dessen das Teilungsverhältnis zwischen den beiden Teilströmen bestimmende Blendenanordnung mit einer zur Vorgabe des Teilungsverhältnisses dienenden ersten Stelleinrichtung versehen ist.The invention relates to a hydraulic circuit arrangement known from DE-A-2751082 and of the generic type with a pressure medium source for supplying a hydro stream, two consumers driven by partial streams of the hydro stream and a proportional flow dividing valve through which the hydro stream and the two partial streams flow, the division ratio between the two orifice arrangement determining the two partial flows is provided with a first actuating device which serves to specify the division ratio.

Mit einer derartigen hydraulischen Schaltungsanordnung können die beiden Verbraucher durch den von einer einzigen, die Druckmittelquelle bildenden Pumpe gelieferten Hydrostrom versorgt werden. Dabei ist es für viele Anwendungen, beispielsweise die Lenkung von Fahrantrieben, erforderlich, das Teilungsverhältnis der den beiden Verbrauchern zugeführten und von dem Proportionalstromteilerventil aus dem Hydrostrom gebildeten beiden Teilströme zu steuern, was mittels der ersten Stelleinrichtung geschieht. Wenngleich sich hierdurch die relative Flussmenge der beiden Teilströme im Verhältnis zueinander einstellen lässt, unterliegt jedoch die Gesamtflussmenge und damit auch die Flussmenge der Teilströme Schwankungen, da der von der Hydropumpe gelieferte Hydrostrom normalerweise nicht konstant ist. Ferner ist selbst bei einer konstanten Gesamtflussmenge des Hydrostroms die Flussmenge der beiden Teilströme nicht steuerbar.With such a hydraulic circuit arrangement, the two consumers can be supplied by the hydraulic current supplied by a single pump which forms the pressure medium source. For many applications, for example the steering of travel drives, it is necessary to control the division ratio of the two partial flows supplied to the two consumers and formed by the proportional flow dividing valve from the hydroflow, which is done by means of the first adjusting device. Although this allows the relative flow volume of the two partial flows to be adjusted in relation to one another, the total flow volume and thus also the flow volume of the partial flows are subject to fluctuations, since the hydraulic flow supplied by the hydraulic pump is normally not constant. Furthermore, even with a constant total flow rate of the hydro stream, the flow rate of the two partial flows cannot be controlled.

Der Erfindung liegt die Aufgabe zugrunde, eine hydraulische Schaltungsanordnung der eingangs genannten Art dahingehend weiterzubilden, dass bei zwei aus einer einzigen Druckmittelquelle mit Teilströmen eines einstellbaren Teilungsverhältnisses beschickten Verbrauchern die Flussmenge einstellbar ist.The invention is based on the object, a hydraulic circuit arrangement of the type mentioned to further develop that the flow quantity can be set in the case of two consumers supplied with partial flows of an adjustable division ratio from a single pressure medium source.

Erfindungsgemäss wird diese Aufgabe dadurch gelöst, dass die Blendenanordnung mit einer zweiten Stelleinrichtung zur Vorgabe ihres Gesamtdurchlassquerschnittes versehen ist und die Druckmittelquelle eine Regeleinrichtung zur lastabhängigen Steuerung des von ihr gelieferten Hydrostroms aufweist, an deren Steuereingang ein der Druckdifferenz zwischen den Drücken beidseits der Blendenanordnung entsprechendes Steuersignal angelegt ist.According to the invention, this object is achieved in that the orifice arrangement is provided with a second actuating device for specifying its total passage cross section, and the pressure medium source has a regulating device for load-dependent control of the hydroflow it supplies, to the control input of which a control signal corresponding to the pressure difference between the pressures on both sides of the orifice arrangement is applied is.

Druckmittelquellen, deren Hydrostrom lastabhängig geregelt ist, sind beispielsweise unter der Bezeichnung LS-Pumpen (Load-Sensing-Pumpen) bekannt. Das zur Regelung der Gesamtflussmenge des von der Druckmittelquelle gelieferten Hydrostroms erforderliche Steuersignal wird bei der Erfindung auf besonders einfache Weise dadurch gewonnen, dass mit der zweiten Stelleinrichtung der Gesamtdurchlassquerschnitt der Blendenanordnung auf einen gewünschten vorgegebenen Wert Fest eingestellt wird. Die bei vorgegebener Einstellung der Blendenanordnung auftretende Druckdifferenz kann somit ohne zusätzliche Schaltungsteile leicht erfasst und als das zur Ansteuerung der Regeleinrichtung erforderliche Steuersignal benutzt werden. Damit können die beiden Verbraucher bei einem geringen baulichen Aufwand mit Teilströmen versorgt werden, bei denen nicht nur das Teilungsverhältnis, sondern auch die Flussmenge auf gewünschte Werte eingestellt sind.Pressure medium sources, the hydroflow of which is regulated depending on the load, are known, for example, under the name LS pumps (load-sensing pumps). The control signal required to regulate the total flow rate of the hydraulic current supplied by the pressure medium source is obtained in a particularly simple manner in the invention by setting the total passage cross section of the orifice arrangement to a desired predetermined value fixed with the second adjusting device. The pressure difference occurring with a predetermined setting of the orifice arrangement can thus easily be detected without additional circuit parts and used as the control signal required to control the control device. This means that the two consumers can be supplied with partial flows with a low level of structural complexity, in which not only the division ratio but also the flow rate are set to the desired values.

In einer bevorzugten Ausführungsform der Erfindung ist vorgesehen, dass zwischen die mit dem Hydrostrom beaufschlagte eine Seite der Blendenanordnung des Proportionalstromteilers und die mit einem der Teilströme beaufschlagte andere Seite der Blendenanordnung zwei zueinander parallel angeordnete Wechselventile geschaltet sind, deren eines den jeweils höheren Druck auf den einen Anschluss des Steuereingangs und deren anderes den jeweils niedrigeren Druck auf den anderen Anschluss des Steuereingangs durchschaltet. Mittels der beiden gegensinnig arbeitenden Wechselventile ist es also möglich, das der Druckdifferenz entsprechende Steuersignal unabhängig von der Flussrichtung im Proportionalstromteiler jeweils gleichsinnig an die betreffenden Anschlüsse des Steuereingangs anzulegen. Damit arbeitet die Schaltungsanordnung auch im Reversierbetrieb, in dem die die beiden Verbraucher durchströmenden Teilströme zum Proportionalstromteilerventil hin gerichtet sind und dort zu dem dann zu einem Tank zurückfliessenden gesamten Hydrostrom vereinigt werden.In a preferred embodiment of the invention it is provided that between the one side of the diaphragm arrangement of the proportional flow divider to which the hydraulic flow is applied and the other side of the orifice arrangement acted on with one of the partial flows, two mutually parallel shuttle valves are connected, one of which switches through the respectively higher pressure on one connection of the control input and the other of which switches the respectively lower pressure on the other connection of the control input. By means of the two reversing valves working in opposite directions, it is therefore possible to apply the control signal corresponding to the pressure difference regardless of the direction of flow in the proportional flow divider in the same direction to the relevant connections of the control input. The circuit arrangement thus also works in reversing mode, in which the partial flows flowing through the two consumers are directed towards the proportional flow dividing valve and are combined there to form the entire hydroflow then flowing back to a tank.

Eine für die hydraulische Schaltungsanordnung besonders zweckmässige Ausgestaltung des Proportionaltromteilerventils besteht darin, dass die Blendenanordnung einen äusseren Hohlkörper und einen darin dichtend gelagerten, in seinem Innenraum von dem Hydrostrom beaufschlagten inneren Hohlkörper aufweist, die mit je zwei von den beiden Teilströmen durchströmten radialen Durchlässen versehen sind, deren den Gesamtdurchlassquerschnitt bestimmende axiale Ueberlappung mittels der zweiten Einstelleinrichtung durch eine gegenseitige Axialverschiebung der beiden Kohlkörper und deren das Teilungsverhältnis bestimmende azimutale Ueberlappung mittels der ersten Einstelleinrichtung durch eine gegenseitige Verdrehung der beiden Hohlkörper einstellbar ist. Bei dieser Ausführungsform wird also die Einstellung der Gesamtflussmenge sowie des Teilungsverhältnisses zwischen den beiden Teilströmen durch den Grad der Ueberlappung der in den beiden Hohlkörpern vorgesehenen radialen Durchlässe bestimmt. In Azimutalrichtung sind die radialen Durchlässe relativ zueinander derart angeordnet, dass bei einer durch die erste Einstelleinrichtung hervorgerufenen gegenseitigen Verdrehung die gemeinsame lichte Oeffnung des einen sich überlappenden Paars radialer Durchlässe in dem Masse abnimmt, wie die gemeinsame lichte Oeffnung des anderen Paares radialer Durchlässe zunimmt, wodurch das Teilungsverhältnis des durch die radialen Durchlässe hindurchtretenden Hydrostroms in seine beiden Teilströme bestimmt ist. Dagegen bewirkt die mittels der zweiten Einstelleinrichtung erfolgende gegenseitige Axialverschiebung der beiden Hohlkörper eine gleichsinnige Veränderung der lichten Oeffnung der einander überlappenden Paare radialer Durchlässe, so dass hierdurch die Gesmtflussmenge eingestellt wird.A configuration of the proportional flow divider valve which is particularly expedient for the hydraulic circuit arrangement consists in the fact that the orifice arrangement has an outer hollow body and an inner hollow body sealingly mounted therein, which is acted upon by the hydraulic flow in its interior and which are each provided with two radial passages through which the two partial flows flow, whose axial overlap determining the total passage cross section can be adjusted by means of the second adjusting device by a mutual axial displacement of the two cabbage bodies and whose azimuthal overlap determining the division ratio can be adjusted by means of the first adjusting device by mutual rotation of the two hollow bodies. In this embodiment, the setting of the total flow rate and the division ratio between the two partial flows is determined by the degree of overlap of the radial passages provided in the two hollow bodies certainly. In the azimuthal direction, the radial passages are arranged relative to one another in such a way that, in the event of a mutual rotation caused by the first adjusting device, the common clear opening of the one overlapping pair of radial passages decreases as the common clear opening of the other pair of radial passages increases, as a result of which the division ratio of the hydroflow passing through the radial passages into its two partial flows is determined. On the other hand, the mutual axial displacement of the two hollow bodies by means of the second adjusting device brings about a change in the same direction of the clear opening of the overlapping pairs of radial passages, so that the total flow rate is thereby set.

Im Rahmen der Erfindung ist auch vorgesehen, dass zwischen die Blendenanordnung und die beiden Verbraucher eine steuerseitig mit den Drücken der beiden Teilströme beaufschlagte Druckwaage geschaltet ist. Da die beiden Verbraucher über die Druckwaage an das Proportionalstromteilerventil angeschlossen sind, sind sie also lastunabhängig geregelt.Within the scope of the invention, it is also provided that a pressure compensator, which is acted upon by the pressure of the two partial flows on the control side, is connected between the orifice arrangement and the two consumers. Since the two consumers are connected to the proportional flow divider valve via the pressure compensator, they are regulated independently of the load.

Für eine baulich einfache Realisierung dieser Massnahme ist vorzugsweise vorgesehen, dass die Druckwaage zwei zueinander spiegelbildlich in einer Bohrung eines Gehäuseblocks axial verschieblich dichtend angeordnete, mit zwei axial beabstandeten radialen Durchlassbereichen versehene Hohlkolben aufweist, die an ihren einander zugewandten, geschlossenen, vom Druck des Hydrostroms beaufschlagten Stirnseiten mit gegenseitig ineinandergreifenden, ihre axiale Relativlage zwischen einer auseinandergezogenen Stellung und einer zusammengeschobenen Stellung begrenzenden Anschlagteilen versehen sind, und dass jeweils der eine Durchlassbereich jedes Hohlkolbens mit einem der Teilströme der Blendenanordnung kommuniziert und der andere Durchlassbereich mit einem an den jeweiligen Verbraucher angeschlossenen und als Steuerkante dienenden radialen Ringraum der Bohrung des Gehäuseblocks zusammenwirkt.For a structurally simple implementation of this measure, it is preferably provided that the pressure compensator has two hollow pistons which are arranged so as to be axially displaceable in a mirror-inverted manner in a bore in a housing block and are provided with two axially spaced radial passage regions and which, on their mutually facing, closed, pressurized by the pressure of the hydraulic flow End faces are provided with mutually interlocking stop parts that limit their axial relative position between an extended position and a pushed-together position, and that each has a passage area of each hollow piston one of the partial flows of the orifice arrangement communicates and the other passage region interacts with a radial annular space in the bore of the housing block which is connected to the respective consumer and serves as a control edge.

In diesem Zusammenhang erweist es sich schliesslich als zweckmässig, dass der Gehäuseblock eine die Bohrung im Bereich zwischen den beiden Hohlkolben der Druckwaage radial durchsetzende weitere Bohrung aufweist, deren auf der einen Seite der die Hohlkolben der Druckwaage aufnehmenden Bohrung offenes Ende einen Anschluss für den Hydrostrom bildet und in deren auf der anderen Seite der die Kohlkolben der Druckwaage aufnehmenden Bohrung gelegenen Abschnitt die Blendenanordnung angeordnet ist. Sowohl die Druckwaage als auch die der Stromteilung dienenden Elemente können somit in einem einzigen Gehäuseblock integriert werden, wodurch die praktische Ausführung der Hydraulikschaltung auf einfache Weise und mit wenig Verbindungsleitungen möglich ist.In this context, it finally proves to be expedient for the housing block to have a further bore which radially penetrates the bore in the region between the two hollow pistons of the pressure compensator and whose open end on one side of the bore receiving the hollow pistons of the pressure compensator forms a connection for the hydroflow and in which on the other side of the section located the bore receiving the cabbage pistons of the pressure compensator is arranged the diaphragm arrangement. Both the pressure compensator and the elements serving to divide the current can thus be integrated in a single housing block, as a result of which the practical implementation of the hydraulic circuit is possible in a simple manner and with few connecting lines.

Weitere Merkmale, Einzelheiten und Vorteile der Erfindung ergeben sich aus der folgenden Beschreibung und der Zeichnung, auf die bezüglich einer erfindungswesentlichen Offenbarung aller im Text nicht erwähnten Einzelheiten ausdrücklich hingewiesen wird. Es zeigt:

Fig. 1
ein Blockdiagramm einer hydraulischen Schaltungsanordnung, und
Fig. 2
eine Schnittansicht eines für die Schaltungsanordnung von Fig. 1 geeigneten Proportionalstromteilerventils.
Further features, details and advantages of the invention will become apparent from the following description and the drawing, to which all details not mentioned in the text are expressly referred with regard to disclosure essential to the invention. It shows:
Fig. 1
a block diagram of a hydraulic circuit arrangement, and
Fig. 2
a sectional view of a proportional flow divider valve suitable for the circuit arrangement of FIG. 1.

Gemäss Fig. 1 dient eine LS-Pumpe (Load-Sensing-Pumpe) 1 zur Lieferung eines lastabhängig gesteuerten Hydrostroms aus einem Hydrauliktank 2. An die LS-Pumpe 1 sind über ein 4/3 Wegeventil 3 und ein Proportionalstromteilerventil 4 zwei Verbraucher 5, 5', angeschlossen, bei denen es sich beispielsweise um hydraulische Antriebsmotoren eines Fahrantriebs oder hydraulische Antriebe von Arbeitsmaschinen verschiedenster Art handeln kann.1, an LS pump (load-sensing pump) 1 is used to deliver a load-dependent controlled hydro stream from a hydraulic tank 2. Two consumers 5, 5 'are connected to the LS pump 1 via a 4/3 way valve 3 and a proportional flow divider valve 4, which are, for example, hydraulic drive motors of a travel drive or hydraulic drives of various types of working machines can.

Das Proportionalstromteilerventil 4 weist eine in Fig. 1 schematisch dargestellte Blendenanordnung 6 auf, an der die Verzweigung zwischen dem an einem Anschluss 7 auftretenden Hydrostrom der LS-Pumpe 1 und den an Anschlüssen 8, 9 auftretenden beiden Teilströmen des Hydrostroms stattfindet. Eine erste Stelleinrichtung 10, die beispielsweise durch ein Magnetstellglied gebildet sein kann, dient zur Einstellung des an der Blendenanordnung 6 auftretenden Teilungsverhältnisses der beiden an den Anschlüssen 8 und 9 auftretenden Teilströme. Ferner greift an der Blendenanordnung 6 eine zweite Stelleinrichtung 11, die ebenfalls durch ein magnetisches Stellglied gebildet sein kann, an, um den Gesamtdurchlassquerschnitt der Blendenanordnung 6 auf einen gewünschten, vorgegebenen Wert einzustellen. Zwischen die Anschlüsse 8, 9 und die Blendenanordnug 6 ist eine Druckwaage 12 geschaltet, die steuerseitig mit den Drücken der beiden an der Blendenanordnung 6 auftretenden Teilströme beaufschlagt ist.The proportional flow divider valve 4 has an orifice arrangement 6, shown schematically in FIG. 1, on which the branching takes place between the hydroflow of the LS pump 1 occurring at a connection 7 and the two partial flows of the hydroflow occurring at connections 8, 9. A first actuating device 10, which can be formed, for example, by a magnetic actuator, serves to set the division ratio of the two partial flows occurring at the ports 8 and 9 at the orifice arrangement 6. Furthermore, a second actuating device 11, which can also be formed by a magnetic actuator, acts on the diaphragm arrangement 6 in order to set the overall passage cross section of the diaphragm arrangement 6 to a desired, predetermined value. A pressure compensator 12 is connected between the connections 8, 9 and the orifice arrangement 6 and is acted upon on the control side by the pressures of the two partial flows occurring at the orifice arrangement 6.

Die Regeleinrichtung der LS-Pumpe 1, die von bekannter Art und daher nicht näher dargestellt ist, weist einen Steuereingang 13 mit zwei Anschlüssen 14, 15 auf, an die ein einer Druckdifferenz entsprechendes Steuersignal derart anzulegen ist, dass der Anschluss 14 jeweils den höheren Druckwert und der Anschluss 15 jeweils den niedrigeren Druckwert empfängt. Als Druckdifferenz dient der an der Blendenanordnung 6 auftretende Druckunterschied, der über Steuerleitungen 16, 17 den Anschlüssen 14, 15 zugeleitet wird.The control device of the LS pump 1, which is of a known type and therefore not shown in detail, has a control input 13 with two connections 14, 15, to which a control signal corresponding to a pressure difference is to be applied in such a way that the connection 14 in each case has the higher pressure value and port 15 receives the lower pressure value. The pressure difference that occurs at the orifice arrangement 6 and the control lines 16, 17 serves as the pressure difference 14, 15 is fed.

Wenn das 4/3 Wegeventil 3 ausgehend von seiner in Fig. 1 dargestellten mittleren Neutralstellung in seine nach rechts verschobene Schaltstellung gebracht wird, findet der Normalbetrieb der hydraulischen Schaltungsanordnung statt, in dem die LS-Pumpe 1 ihren Hydrostrom zum Anschluss 7 des Proportionalstromteilerventils 4 fördert, welches den Hydrostrom entsprechend der durch die erste Stelleinrichtung 10 vorgegebenen Einstellung in die beiden in einem gewissen Verhältnis zueinander stehenden Teilströme aufteilt und mittels der Steuerkanten der Druckwaage 12 lastunabhängig geregelt den Verbrauchern 5, 5' zuführt, von wo aus die beiden Teilströme über eine gemeinsame Leitung 18 und das 4/3 Wegeventil 3 zum Hydrauliktank 2 zurückfliesen. In diesem Fall des Normalbetriebs tritt also an der dem Anschluss 7 zugewandten Seite der Blendenanordnung 6 ein höherer Druckwert auf als an der dem Anschluss 7 abgewandten Seite der Blendenanordnung 6, wobei der Druckunterschied von dem durch die zweite Stelleinrichtung 11 vorgegebenen Gesamtdurchlassquerschnitt der Blendenanordnung 6 abhängt. Andererseits kehrt sich jedoch beim Reversierbetrieb, bei dem das 4/3 Wegeventil 3 seine nach links verschobene Schaltstellung einnimmt, die Flussrichtung um, so dass dann der höhere Druckwert an der dem Anschluss 7 abgekehrten Seite der Blendenanordnung 6 und der niedrigere Druckwert an der dem Anschluss 7 zugekehrten Seite auftritt.If the 4/3 directional control valve 3 is moved from its middle neutral position shown in FIG. 1 to its shift position shifted to the right, the hydraulic circuit arrangement operates normally, in which the LS pump 1 promotes its hydroflow to the connection 7 of the proportional flow divider valve 4 , which divides the hydraulic flow according to the setting specified by the first adjusting device 10 into the two partial flows that are in a certain relationship to one another and by means of the control edges of the pressure compensator 12 supplies the consumers 5, 5 'in a controlled manner, from where the two partial flows via a common one Tile line 18 and the 4/3 way valve 3 back to the hydraulic tank 2. In this case of normal operation, a higher pressure value occurs on the side of the orifice arrangement 6 facing the connection 7 than on the side of the orifice arrangement 6 facing away from the connection 7, the pressure difference depending on the total passage cross section of the orifice arrangement 6 specified by the second adjusting device 11. On the other hand, however, the direction of flow reverses in reversing operation, in which the 4/3 way valve 3 assumes its switching position shifted to the left, so that the higher pressure value on the side of the orifice arrangement 6 facing away from the connection 7 and the lower pressure value on the connection 7 facing side occurs.

Um den Anschlüssen 14, 15 des Steuereingangs 13 das der Druckdifferenz entsprechende Steuersignal stets im richtigen Richtungssinn zuzuführen, ist zwischen die beiden Seiten der Blendenanordnung 6 eine Parallelschaltung aus zwei Wechselventilen 19, 20 geschaltet. Das Wechselventil 19 ist derart aufgebaut, dass es den jeweils höheren Druckwert auf einen mit der Steuerleitung 16 verbundenen Anschluss 21 durchschaltet, während das wechselventil 20 den jeweils niedrigeren Druckwert auf einen Anschluss 22 durchschaltet, an den die Steuerleitung 17 angeschlossen ist. Dadurch ist in beiden Betriebsarten, nämlich Normalbetrieb und Reversierbetrieb, die sinnrichtige Durchschaltung des Steuersignals an den Steuereingang der LS-Pumpe 1 sichergestellt.In order to always supply the control signal corresponding to the pressure difference to the connections 14, 15 of the control input 13 in the correct direction, a parallel connection of two shuttle valves 19, 20 is connected between the two sides of the orifice arrangement 6. The shuttle valve 19 is constructed in such a way that it connects the higher pressure value to the control line 16 Connection 21 switches through, while the shuttle valve 20 switches through the respectively lower pressure value to a connection 22 to which the control line 17 is connected. This ensures that the control signal is properly switched through to the control input of the LS pump 1 in both operating modes, namely normal operation and reversing operation.

Aus der Schnittdarstellung von Fig. 2 geht eine Ausführungsform des für die hydraulische Schaltung bestimmten Proportionalstromteilerventil 4 hervor, bei dem die Blendenanordnung 6 und die Druckwaage 12 in einem gemeinsamen Gehäuseblock 23 zusammengebaut sind. Zu diesem Zweck weist der Gehäuseblock 23 eine sich in der Darstellung von Fig. 2 mit ihrer Achse horizontal erstreckende Bohrung 24 und eine die Bohrung 24 in der Mitte ihrer axialen Länge senkrecht kreuzende weitere Bohrung 25 auf. In der weiteren Bohrung 25 ist ein äusserer Hohlkörper 26 der Blendenanordnung 6 axial unverschieblich, jedoch um die Achse in azimutaler Richtung um einen bestimmten Winkelbetrag drehbar gelagert. Diese Winkeldrehung des Hohlkörpers 26 erfolgt im Ausführungsbeispiel von Fig. 2 durch eine mit dem Aussenmantel des Kohlkörpers 26 in Eingriff stehende Schneckenspindel 27, deren Verlängerungsachse senkrecht zur Zeichenebene aus dem Gehäuseblock 23 herausgeführt ist und die erste Stelleinrichtung 10 bilet. In dem äusseren Hohlkörper 26 ist ein innerer Hohlkörper 28 dichtend gelagert, der durch einen in einer Längsnut 29 des Gehäuseblocks 23 geführten radialen Nocken 30 in dem Gehäuseblock 23 drehfest abgestützt ist.2 shows an embodiment of the proportional flow divider valve 4 intended for the hydraulic circuit, in which the orifice arrangement 6 and the pressure compensator 12 are assembled in a common housing block 23. For this purpose, the housing block 23 has a bore 24 extending horizontally with its axis in the illustration in FIG. 2 and a further bore 25 crossing the bore 24 perpendicularly in the middle of its axial length. In the further bore 25, an outer hollow body 26 of the diaphragm arrangement 6 is axially immovable, but is rotatable about the axis in the azimuthal direction by a certain angular amount. This angular rotation of the hollow body 26 takes place in the exemplary embodiment of FIG. 2 by a worm spindle 27 which engages with the outer casing of the hollow body 26, the extension axis of which is led out of the housing block 23 perpendicular to the plane of the drawing and the first actuating device 10 is shown. In the outer hollow body 26, an inner hollow body 28 is sealingly supported, which is supported in a rotationally fixed manner in the housing block 23 by a radial cam 30 guided in a longitudinal groove 29 of the housing block 23.

Als zweite Stelleinrichtung 11 dient ein das in Fig. 2 obere Ende der weiteren Bohrung 25 abschliessendes Verschlussteil, das ein axial verstellbares Stellglied 31 aufweist. Durch die Axialbewegung des Stellglieds 31 wird der innere Hohlkörper 28 entgegen der rückführenden Kraft einer Rückholfeder 32 gegenüber dem äusseren Hohlkörper 26 axial verschoben.A closing part which closes the upper end of the further bore 25 in FIG. 2 and has an axially adjustable actuator 31 serves as the second adjusting device 11. By the axial movement of the actuator 31st the inner hollow body 28 is axially displaced against the returning force of a return spring 32 with respect to the outer hollow body 26.

Der äussere und der innere Hohlkörper 26 bzw. 28 sind mit je zwei radialen Durchlässen 33, 33' bzw. 34, 34' versehen, deren gegenseitige Ueberlappung in axialer Richtung durch das Stellglied 31 und in azimutaler Richtung durch die Schneckenspindel 27 eingestellt wird. Durch eine Drehung der Schneckenspinkel 27 verringert sich die durch die Ueberlappung der radialen Durchlässe 33, 34 bestimmte lichte Durchlassöffnung in dem Masse, wie sich die durch die Ueberlappung der radialen Durchlässe 33', 34' bestimmte lichte Durchlassöffnung vergrössert. Durch die axiale Verschiebung des inneren Hohlkörpers 28 gegenüber dem äusseren Hohlkörper 26 wird dagegen der Gesamtdurchlassquerschnitt der durch die Uebelappungen der radialen Durchlässe 33, 34 bzw. 33', 34' bestimmte Gesamtdurchlassquerschnitt eingestellt.The outer and the inner hollow body 26 and 28 are each provided with two radial passages 33, 33 'and 34, 34', the mutual overlap of which is set in the axial direction by the actuator 31 and in the azimuthal direction by the worm spindle 27. By rotating the screw angles 27, the clear passage opening determined by the overlap of the radial passages 33, 34 is reduced to the same extent as the clear passage opening determined by the overlap of the radial passages 33 ', 34'. By means of the axial displacement of the inner hollow body 28 relative to the outer hollow body 26, on the other hand, the total passage cross section is determined by the total passage cross section determined by the lobes of the radial passages 33, 34 and 33 ', 34'.

In der Normalbetriebsart strömt also der von der LS-Pumpe 1 erzeugte Hydraulikstrom durch das den Anschluss 7 von Fig. 1 bildende offene Ende der weiteren Bohrung 25, welches dem mit dem Stellglied 31 versehenen geschlossenen Ende entgegengesetzt ist, in den Innenraum des inneren Hohlkörpers 28 ein und tritt durch die radialen Durchlässe 33, 34 bzw. 33', 34' hindurch. An mit den radialen Durchlässen 33, 33' des äusseren Hohlkörpers 26 kommunizierenden Kanälen 35, 35' des Gehäuseblocks 23 stehen damit die hinsichtlich der Gesamtflussmenge und des Teilungsverhältnisses eingestellten Teilströme des Hydraulikstroms zur Verfügung.In the normal operating mode, the hydraulic flow generated by the LS pump 1 thus flows through the open end of the further bore 25 forming the connection 7 of FIG. 1, which is opposite the closed end provided with the actuator 31, into the interior of the inner hollow body 28 enters and passes through the radial passages 33, 34 and 33 ', 34'. The partial flows of the hydraulic flow which are set with regard to the total flow quantity and the division ratio are thus available on channels 35, 35 'of the housing block 23 which communicate with the radial passages 33, 33' of the outer hollow body 26.

In der zur weiteren Bohrung 25 orthogonalen Bohrung 24, die an ihren beiden Enden durch Verschlussschrauben 36, 36' abgeschlossen ist, sind zwei in der Längsachse der Bohrung 24 einander spiegelbildlich gegenüberstehende Hohlkolben 37, 37' axial verschieblich und dichtend angeordnet. Jeder Hohlkolben 37, 37' weist zwei voneinander axial beabstandete radiale Durchlassbereiche 38, 39 bzw. 38', 39' auf, von denen die von den Verschlussschrauben 36, 36' weiter entfernt gelegenen radialen Durchlassbereiche 38 bzw. 38' mit den in die Bohrung 24 mündenden Kanälen 35 bzw. 35' kommunizieren. Dagegen wirken die den Verschlussschrauben 36, 36' jeweils näher gelegenen radialen Durchlassbereiche 39, 39' mit radialen Ringräumen 40 bzw. 40' in der Bohrung 24 zusammen, wobei diese radialen Ringräume 40, 40' über innere Kanäle 41, 41' mit den in dem Gehäuseblock 23 vorgesehenen äusseren Anschlüssen 8 bzw. 9 verbunden sind. Die axiale Lage der radialen Durchlassbereiche 39, 39' in bezug auf die radialen Ringräume 40 bzw. 40' ist dabei derart gewählt, dass die Begrenzungskanten der Ringräume 40 bzw. 40' als Steuerkanten mit den radialen Durchlassbereichen 39, 39' zusammenwirken, sobald die Kohlkolben 37, 37' unter dem Einfluss der Druckverhältnisse aus ihrer zur Achse der weiteren Bohrung 25 symmetrischen Mittellage verschoben werden. Im einzelnen sind alle radialen Durchlassbereiche 38, 38', 39, 39' jeweils durch eine bestimmte Anzahl von Löchern gebildet, die unter gleichem winkelabstand um den Umfang der Hohlkolben 37, 37' herum verteilt sind.In the bore 24 orthogonal to the further bore 25, which is closed at both ends by screw plugs 36, 36 ', two are in the longitudinal axis of the Bore 24 opposite to each other mirror-inverted hollow pistons 37, 37 'axially displaceable and sealed. Each hollow piston 37, 37 'has two radial passage regions 38, 39 and 38', 39 ', axially spaced apart from one another, of which the radial passage regions 38 and 38', which are further away from the locking screws 36, 36 ', with those into the bore 24 opening channels 35 and 35 'communicate. In contrast, the radial passage regions 39, 39 ', which are respectively closer to the locking screws 36, 36', cooperate with radial annular spaces 40 and 40 'in the bore 24, these radial annular spaces 40, 40' via inner channels 41, 41 'with those in FIGS the outer connections 8 and 9 provided to the housing block 23 are connected. The axial position of the radial passage areas 39, 39 'with respect to the radial annular spaces 40 and 40' is selected such that the boundary edges of the annular spaces 40 and 40 'act as control edges with the radial passage areas 39, 39' as soon as the Cabbage pistons 37, 37 'are displaced from their central position symmetrical to the axis of the further bore 25 under the influence of the pressure conditions. In detail, all radial passage areas 38, 38 ', 39, 39' are each formed by a certain number of holes which are distributed around the circumference of the hollow pistons 37, 37 'at the same angular distance.

An ihren einander zugewandten Stirnseiten sind die Hohlkolben 37, 37' jeweils mit hakenförmigen Anschlagteilen 42, 42' versehen, die in einer maximal auseinandergezogenen Stellung der beiden Hohlkolben 37, 37' ineinandergreifend aneinander anschlagen und dadurch eine weitere Trennbewegung der Hohlkolben 37, 37' begrenzen. Dagegen stützt sich in einer maximal zusammengeschobenen Stellung jeweils das Anschlagteil 42 des Hohlkolbens 37 an der Stirnseite des anderen Hohlkolbens 37' ab, und umgekehrt, so dass auch in der maximal zusammengeschobenen Stellung der beiden Hohlkolben 37, 37' zwischen ihren einander zugewandten Stirnseiten noch ein lichter Durchlass besteht.On their mutually facing end faces, the hollow pistons 37, 37 'are each provided with hook-shaped stop parts 42, 42' which, when the two hollow pistons 37, 37 'are in a maximally extended position, abut one another and thereby limit a further separating movement of the hollow pistons 37, 37' . In contrast, the stop part 42 of the hollow piston 37 is supported on the end face of the other hollow piston 37 'in a maximally pushed-together position, and vice versa, so that even in the maximally pushed-together position of the two hollow pistons 37, 37 'there is still a clear passage between their mutually facing end faces.

Im Normalbetrieb fördert also die LS-Pumpe 1 den Hydrostrom in Richtung des Pfeiles 43 durch den zwischen den beiden Hohlkolben 37, 37' der Druckwaage 12 in der weiteren Bohrung 25 freigelassenen Kanal hindurch zum Innenraum des inneren Hohlkörpers 28 der Blendenanordnung 6, wodurch sich die beiden Hohlkolben 37, 37' in ihre auseinandergezogene Stellung verschieben. Die an der Blendenanordnung 6 auftretenden Teilströme des Hydrostroms werden über die Kanäle 35 bzw. 35', die radialen Durchlassbereiche 38 bzw. 38' und die radialen Durchlässe 39 bzw. 39' den Ringräumen 40 bzw. 40' zugeführt und durch die von diesen gebildeten Steuerkanten lastunabhängig konstant gehalten sowie den Anschlüssen 8 und 9 zugeführt. Im Reversierbetrieb, bei dem die Flussrichtung umgekehrt wird, treten dagegen die beiden Teilströme an den Anschlüssen 7 und 8 ein und gelangen über die sodann zusammengeschobenen Hohlkolben 37, 37' und die Blendenanordnung 6 zum Anschluss 7, wo sodann der gesamte Hydrostrom austritt.In normal operation, therefore, the LS pump 1 promotes the hydraulic flow in the direction of arrow 43 through the channel left between the two hollow pistons 37, 37 'of the pressure compensator 12 in the further bore 25 to the interior of the inner hollow body 28 of the orifice arrangement 6, as a result of which the move the two hollow pistons 37, 37 'into their extended positions. The partial flows of the hydroflow occurring at the orifice arrangement 6 are supplied to the annular spaces 40 and 40 'via the channels 35 and 35', the radial passage areas 38 and 38 'and the radial passages 39 and 39' and are formed by the latter Control edges are kept constant regardless of load and fed to connections 8 and 9. In reverse operation, in which the direction of flow is reversed, on the other hand, the two partial flows occur at the connections 7 and 8 and reach the connection 7 via the hollow pistons 37, 37 ′ then pushed together and the orifice arrangement 6, where the entire hydroflow then emerges.

Claims (6)

  1. Hydraulic circuit comprising a hydraulic medium source (1) for supplying a hydraulic flow, two consumers (5, 5') driven by partial flows of the hydraulic flow and a proportional flow distributing valve (4) traversed by the hydraulic flow and the two partial flows, the diaphragm arrangement (6) thereof determining the flow distribution ratio between the two partial flows being provided with a first regulating device (10) serving to predetermine the flow distribution ratio, characterised in that the diaphragm arrangement (6) is provided with a second regulating device (11) for predetermining its total through-flow cross section and the hydraulic medium source (1) has a control device for the load-dependent control of the hydraulic flow supplied thereby, to the control input (13) of which a control signal corresponding to the pressure difference between the pressures on either side of the diaphragm arrangement (6) is fed.
  2. Hydraulic circuit according to claim 1, characterised in that two shuttle valves (19, 20) arranged in parallel are connected between one side of the diaphragm arrangement (6) of the proportional flow distributing valve (4) acted upon by the hydraulic flow and the other side of the diaphragm arrangement (6) acted upon by one of the partial flows, one (19) of which connects the respectively higher pressure to one connection (14) of the control input (13) and the other (20) of which connects the respectively lower pressure to the other connection (15) of the control input (15).
  3. Hydraulic circuit according to claim 1 or claim 2, characterised in that the diaphragm arrangement has an outer hollow body (26) and an inner hollow body (28) supported therein in a sealed manner and acted upon in its inner space by the hydraulic flow, these hollow bodies each being provided with two radial openings (33, 34; 33', 34') traversed by the partial flows, the axial overlapping thereof defining the total through-flow cross section being adjustable by means of the second regulating device (11; 31) by mutual axial displacement of the two hollow bodies (26, 28) and the azimuthal overlapping thereof defining the flow distribution ratio being adjustable by means of the first regulating device (10; 27) by mutual rotation of the two hollow bodies (26, 28).
  4. Hydraulic circuit according to one of claims 1 to 3, characterised in that a compensator (12) acted upon at the control side by the pressures of the two partial flows is connected between the diaphragm arrangement (6) and the two consumers (5, 5').
  5. Hydraulic circuit according to claim 4, characterised in that the compensator has two hollow pistons (37, 37') arranged in an axially displaceable and sealed manner in a bore (24) of a housing block (23) in a mirror-inverted manner relative to one another, and provided with two radial opening regions (38, 38'; 39, 39') at an axial distance from one another, these hollow pistons being provided at their closed end faces facing one another and acted upon by the pressure of the hydraulic flow with mutually engaging stop parts defining their relative axial positions between an extended position and a telescoped position, and that one respective opening region (38, 38') of each hollow piston (37, 37') communicates with one of the partial flows of the diaphragm arrangement (6) and the other opening region (39, 39') cooperates with a radial annular space (40; 40') of the bore (24) of the housing block (23) connected to the respective consumer (5, 5') and serving as a metering edge.
  6. Hydraulic circuit according to claim 5, characterised in that the housing block (23) has a further bore (25) radially traversing the bore (24) in the region between the two hollow pistons (37, 37') of the compensator (12), the end of the bore (25) open at one side of the bore (24) receiving the hollow pistons (37, 37') of the compensator (12) forming a connection (7) for the hydraulic flow and the diaphragm arrangement (6) being arranged in its section placed at the other side of the bore (24) receiving the hollow pistons (37, 37') of the compensator (12).
EP90900115A 1988-11-18 1989-11-18 Hydraulic circuit Expired - Lifetime EP0397840B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH4288/88 1988-11-18
CH428888A CH676347A5 (en) 1988-11-18 1988-11-18
PCT/EP1989/001396 WO1990005853A1 (en) 1988-11-18 1989-11-18 Hydraulic circuit

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EP0397840A1 EP0397840A1 (en) 1990-11-22
EP0397840B1 true EP0397840B1 (en) 1994-06-22

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EP90900115A Expired - Lifetime EP0397840B1 (en) 1988-11-18 1989-11-18 Hydraulic circuit

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EP (1) EP0397840B1 (en)
CH (1) CH676347A5 (en)
DE (1) DE58907963D1 (en)
WO (1) WO1990005853A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0879753A2 (en) 1997-05-23 1998-11-25 Agria-Werke GmbH Vehicle with hydraulic individual wheel drive

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101975201A (en) * 2010-11-02 2011-02-16 赵国普 Single-pump multi-executing mechanism hydraulic control system
CN103671333B (en) * 2013-11-25 2016-03-30 湘潭市恒欣实业有限公司 The pump hydraulic station that can automatically switch

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3979908A (en) * 1975-09-29 1976-09-14 The Cessna Aircraft Company Priority flow valve
US4085766A (en) * 1976-04-15 1978-04-25 Bourns, Inc. Adjustable gas mixing valve
DE2751082C2 (en) * 1977-11-16 1982-12-02 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Flow divider valve for a hydraulic system
DE2818360A1 (en) * 1978-04-26 1979-11-08 Johann Ing Grad Tyroller Adjustable liq. flow divider for hydraulic systems - has two throttles whose cross=sections can be varied while retaining their sum constant
CA1192811A (en) * 1982-08-02 1985-09-03 Modular Controls Corporation Flow divider-combiner valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0879753A2 (en) 1997-05-23 1998-11-25 Agria-Werke GmbH Vehicle with hydraulic individual wheel drive

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EP0397840A1 (en) 1990-11-22
WO1990005853A1 (en) 1990-05-31
DE58907963D1 (en) 1994-08-04
CH676347A5 (en) 1991-01-15

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