EP2672125B1 - Hydraulic system for the reliable pressure supply to at least one consumer - Google Patents

Hydraulic system for the reliable pressure supply to at least one consumer Download PDF

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Publication number
EP2672125B1
EP2672125B1 EP13001739.5A EP13001739A EP2672125B1 EP 2672125 B1 EP2672125 B1 EP 2672125B1 EP 13001739 A EP13001739 A EP 13001739A EP 2672125 B1 EP2672125 B1 EP 2672125B1
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EP
European Patent Office
Prior art keywords
pressure
consumer
pump
displacement pump
hydraulic system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP13001739.5A
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German (de)
French (fr)
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EP2672125A2 (en
EP2672125A3 (en
Inventor
Josef Scholl
Heinz-Peter Huth
Marc Anton
Markus Mohrbacher
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Hydac Systems and Services GmbH
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Hydac Systems and Services GmbH
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Publication date
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Publication of EP2672125A2 publication Critical patent/EP2672125A2/en
Publication of EP2672125A3 publication Critical patent/EP2672125A3/en
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Classifications

    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/265—Control of multiple pressure sources
    • F15B2211/2654—Control of multiple pressure sources one or more pressure sources having priority
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • F15B2211/5152—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve being connected to multiple pressure sources
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the invention relates to a hydraulic system for reliably supplying pressure to at least one consumer.
  • the DE 41 29 508 A1 describes a hydraulic system for the safe pressure supply of at least one consumer with the features in the preamble of claim 1 with a constant pump that provides a delivery flow for the consumer, an additional pump and a valve arrangement, by means of which, depending on a load pressure of the consumer in question whose supply requirement exceeds the full flow rate of the fixed displacement pump, the additional pump can be connected to the consumer, the valve arrangement having a pressure compensator, with the pressure of the fixed displacement pump on the one hand, and thus the pressure at the supply connection of the consumer, and on the other hand the load pressure of the consumer plus on the valve piston of the pressure compensator a spring pressure are present and the additional pump is connected via the pressure compensator to the supply connection of the consumer in control positions of the pressure compensator in which the pressure of the constant pump is lower than the load pressure plus the spring pressure.
  • the invention is based on the object of providing a hydraulic system containing a fixed displacement pump, which enables a reliable pressure supply to the relevant consumers in a particularly economical manner.
  • An essential feature of the invention is accordingly that the pressure compensator is provided in the form of a 4/3-way valve, with the constant pump on one of its inflow-side connections, the control pump on the other inflow-side connection and the supply connection of the consumer and on one outflow-side connection a line leading to the tank is connected to the other downstream connection.
  • the consumer is normally supplied by the fixed displacement pump as long as it can maintain the pressure balance between the supply pressure of the consumer and its load pressure, plus the spring pressure acting on the pressure compensator. If the consumer requires a volume flow above the full flow rate of the fixed displacement pump, so that this pressure equilibrium is not maintained, then the spring moves the valve piston of the pressure compensator into control positions in which a connection is established between the additional pump and the supply connection of the consumer.
  • the system has an additional pump in addition to the fixed displacement pump and that a valve arrangement is provided by means of which the additional pump can be switched on to the consumer as a function of a load pressure of the consumer in question, at which the supply requirement exceeds the full flow rate of the fixed displacement pump.
  • a valve arrangement is provided by means of which the additional pump can be switched on to the consumer as a function of a load pressure of the consumer in question, at which the supply requirement exceeds the full flow rate of the fixed displacement pump.
  • the hydraulic system according to the invention can be provided with particular advantage for supplying a hydraulically actuated steering system of a vehicle.
  • At least one further consumer of lower priority can be assigned to the system, with such a consumer of lower priority either by a volume flow from the auxiliary pump or constant pump can be supplied.
  • an additional pump in the form of a regulating pump can be provided, with at least one of the consumers of lower priority for the supply by the regulating pump being able to be connected to the latter.
  • the arrangement can be made such that the load pressure of the steering and the highest load pressure of the consumers connected to the control pump with lower priority are present at a shuttle valve that supplies the respective dominant load pressure to the controller of the control pump.
  • the regulating pump preferably in the form of a volume flow-regulated piston pump, the supply pressure for the respective consumer with lower priority can be adjusted to the current pressure level of the consumer with the highest load pressure.
  • the current pressure of the control pump can be significantly higher than the required supply pressure of the steering.
  • a lower priority consumer for example in the form of a cooler, can be arranged in the line leading from the pressure compensator to the tank.
  • the invention is explained using an example in which the hydraulically actuated steering system 1 of a vehicle is to be supplied with hydraulic pressure as a first priority consumer.
  • the system has a fixed displacement pump 3 and a control pump 5 for this purpose.
  • the fixed displacement pump 3 is formed by a gear pump, and a volume flow-controlled piston pump is provided as the control pump 5.
  • the pressure-side output of the fixed displacement pump 3 is connected to the supply connection PL of the steering system 1 via a supply line 7.
  • this has a load-sensing connection LS, which carries the respective load pressure.
  • a tank connection T of the steering system 1 is connected to the tank.
  • the regulating pump 5 is connected at its pressure-side connection via a line 9 to an individual pressure compensator 11, which in the present example is a 4/3-way valve with two control edges and a continuous function.
  • the pressure compensator 11 has two inflow-side connections, at one of which Connection 13, the output side of the fixed displacement pump 3 and a control line 15 are connected, the control pressure of which, which corresponds to the pressure of the fixed displacement pump 3 and thus the pressure at the supply connection PL of the steering system 1, acts on one side of the valve piston of the pressure compensator 11.
  • the second connection 17 on the inflow side of the pressure compensator 11 is connected to the line 9 at the outlet of the regulating pump 5 on the pressure side.
  • a first downstream connection 19 is connected via a check valve 21 to the supply line 7 and thus to the supply connection PL of the steering system 1.
  • a line 24 is connected to the second downstream connection 22 of the pressure compensator 11 and leads to the tank via a cooler.
  • the end of the valve piston of the pressure compensator 11 opposite the control line 15 is acted upon by the load pressure of the steering 1, which is supplied from the load-sensing connection LS via a control line 25, and by the pressure of a spring 23.
  • the control line 25 carrying the load pressure is also connected via a connecting line 27 to one side of a shuttle valve 29 to which a load pressure line 31 is connected on the other hand.
  • This guides the load pressure of further consumers assigned to the system, which are assigned to the system and are supplied by the regulating pump 5 via a pressure line 33 connected to its outlet on the pressure side.
  • the additional consumers can be, for example, level control, suspension / damping, a braking device or the like.
  • the shuttle valve 29 compares the load pressure of the steering 1 on the connecting line 27 with the highest load pressure of the other consumers on the load pressure line 31 and reports the dominant pressure to the regulator connection 35 of the regulating pump 5. This regulates the supply pressure in the supply line 9 , which is present at the connection 7 of the pressure compensator 11, to at least the load pressure of the steering 1 plus the control pressure difference of the controller of the control pump 5.
  • the pressure compensator 11 is set to the Fig. 1 and 2 control positions shown.
  • the position corresponds to Fig. 1 the operating state at a load pressure of the steering system 1, in which the excess volume flow of the fixed displacement pump 3 flows off via the inflow-side connection 13 and the outflow-side connection 22 of the pressure compensator 1 to the tank.
  • the connection to the regulating pump 5 via the supply line 9 is blocked.
  • the Fig. 2 shows the operating state in which the connection to the regulating pump 5 is still blocked, there is pressure equilibrium at the pressure compensator 11 and the steering system 1 is only supplied by the fixed displacement pump 3 via the supply line 7.
  • the valve piston At the given load pressure of the steering 1, which is effective via the control line 25 on the valve piston of the pressure compensator 11 together with the pressure of the spring 23, the valve piston is against the weaker effect of the pressure of the constant pump 3, which is supplied via the control line 15, to the left in the normal position of Fig. 3 postponed.
  • the regulating pump 5 is connected to the supply connection PL of the steering system 1 via the supply line 9 and the downstream connection 19 of the pressure compensator 11 and via the check valve 21.
  • the regulating pump 5 can be regulated to an output pressure which is significantly above the required supply pressure of the steering system 1.
  • the output pressure of the control pump 5 via the supply line 9, the connections 17 and 19 as well as the check valve 21 and the supply line 7 is also present at the inflow-side connection 13 and is therefore also effective on the valve piston of the pressure compensator 11 via the control line 15, the steering system 1 is only supplied with the supply pressure that corresponds to the prevailing load pressure of the steering system 1 plus the pressure of the spring 23, regardless of the pump pressure of the regulating pump 5.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Die Erfindung betrifft ein Hydrauliksystem zur sicheren Druckversorgung mindestens eines Verbrauchers.The invention relates to a hydraulic system for reliably supplying pressure to at least one consumer.

Bei Hydrauliksystemen, bei denen mittels einer Konstantpumpe Verbraucher zu versorgen sind, die im Betrieb unterschiedlich stark belastet sind, so dass sich als Load-Sensing-Signal unterschiedliche Lastdrücke ergeben, ist die sichere Druckversorgung so lange gewährleistet, als die Konstantpumpe in der Lage ist, einen dem höchsten Lastdruck entsprechenden Versorgungsdruck bei vollem Förderstrom der Konstantpumpe aufrecht zu erhalten. Wenn der Versorgungsbedarf über dem momentanen Förderstrom der Konstantpumpe liegt, droht Unterversorgung mit entsprechend nachteiligen Auswirkungen auf die Betriebssicherheit. Wenn es sich um Verbraucher handelt, deren Funktion aus Sicherheitsgründen unbedingt gewährleistet sein muss, beispielsweise im Falle von Hydrolenkungen, ist dies nicht hinnehmbar. Um dieser Schwierigkeit zu entgehen, kann die Konstantpumpe für eine entsprechend hohe Förderleistung ausgelegt werden. Neben der sich ergebenden hohen Anlagekosten ist hierbei auch nachteilig, dass in den Betriebsphasen, bei denen nur geringe oder fast keine Lastdrücke gegeben sind, ein entsprechend großer, nicht benötigter Volumenstrom ungenutzt, oder beispielsweise über einen Kühler, zum Tank abfließt.In hydraulic systems in which consumers are to be supplied by means of a constant pump that are subject to different loads during operation, so that different load pressures result as a load-sensing signal, the reliable pressure supply is guaranteed as long as the constant pump is able to to maintain a supply pressure corresponding to the highest load pressure at full flow rate of the fixed displacement pump. If the supply requirement is above the current flow rate of the fixed displacement pump, there is a risk of undersupply with correspondingly detrimental effects on operational safety. When it comes to consumers whose function must be guaranteed for safety reasons, for example in the case of hydraulic steering systems, this is unacceptable. In order to avoid this difficulty, the fixed displacement pump can be designed for a correspondingly high delivery rate. In addition to the resulting high investment costs, it is also disadvantageous that in the operating phases in which there are only low or almost no load pressures, a correspondingly large volume flow that is not required is unused or, for example, flows off to the tank via a cooler.

Die DE 41 29 508 A1 beschreibt ein Hydrauliksystem zur sicheren Druckversorgung mindestens eines Verbrauchers mit den Merkmalen im Oberbegriff von Anspruch 1 mit einer Konstantpumpe, die für den Verbraucher einen Förderstrom zur Verfügung stellt, einer Zusatzpumpe und einer Ventilanordnung, mittels deren in Abhängigkeit von einem Lastdruck des betreffenden Verbrauchers, bei dem dessen Versorgungsbedarf den vollen Förderstrom der Konstantpumpe übersteigt, die Zusatzpumpe dem Verbraucher zuschaltbar ist, wobei die Ventilanordnung eine Druckwaage aufweist, wobei am Ventilkolben der Druckwaage einerseits der Druck der Konstantpumpe, und damit der Druck am Versorgungsanschluss des Verbrauchers, und andererseits der Lastdruck des Verbrauchers plus einem Federdruck anstehen und wobei über die Druckwaage die Zusatzpumpe mit dem Versorgungsanschluss des Verbrauchers bei Regelpositionen der Druckwaage verbunden ist, bei denen der Druck der Konstantpumpe geringer ist als der Lastdruck plus dem Federdruck.the DE 41 29 508 A1 describes a hydraulic system for the safe pressure supply of at least one consumer with the features in the preamble of claim 1 with a constant pump that provides a delivery flow for the consumer, an additional pump and a valve arrangement, by means of which, depending on a load pressure of the consumer in question whose supply requirement exceeds the full flow rate of the fixed displacement pump, the additional pump can be connected to the consumer, the valve arrangement having a pressure compensator, with the pressure of the fixed displacement pump on the one hand, and thus the pressure at the supply connection of the consumer, and on the other hand the load pressure of the consumer plus on the valve piston of the pressure compensator a spring pressure are present and the additional pump is connected via the pressure compensator to the supply connection of the consumer in control positions of the pressure compensator in which the pressure of the constant pump is lower than the load pressure plus the spring pressure.

Weitere Hydrauliksysteme gehen aus der US 5 918 558 und der EP 0 989 048 A1 hervor.Other hydraulic systems go out of the U.S. 5,918,558 and the EP 0 989 048 A1 emerged.

Im Hinblick auf diese Problematik liegt der Erfindung die Aufgabe zugrunde, ein eine Konstantpumpe enthaltendes Hydrauliksystem zur Verfügung zu stellen, das auf besonders wirtschaftliche Weise eine sichere Druckversorgung betreffender Verbraucher ermöglicht.With regard to this problem, the invention is based on the object of providing a hydraulic system containing a fixed displacement pump, which enables a reliable pressure supply to the relevant consumers in a particularly economical manner.

Erfindungsgemäß ist diese Aufgabe durch ein Hydrauliksystem gelöst, das die Merkmale des Patentanspruchs 1 in seiner Gesamtheit aufweist.According to the invention, this object is achieved by a hydraulic system which has the features of claim 1 in its entirety.

Eine wesentliche Besonderheit der Erfindung besteht demgemäß darin, dass die Druckwaage in Form eines 4/3-Wege-Ventils vorgesehen ist, wobei am einen ihrer zuströmseitigen Anschlüsse die Konstantpumpe, am anderen zuströmseitigen Anschluss die Regelpumpe und am einen abströmseitigen Anschluss der Versorgungsanschluss des Verbrauchers und am anderen abströmseitigen Anschluss eine zum Tank führende Leitung angeschlossen sind.An essential feature of the invention is accordingly that the pressure compensator is provided in the form of a 4/3-way valve, with the constant pump on one of its inflow-side connections, the control pump on the other inflow-side connection and the supply connection of the consumer and on one outflow-side connection a line leading to the tank is connected to the other downstream connection.

Bei dieser Anordnung erfolgt die Versorgung des Verbrauchers normalerweise durch die Konstantpumpe, so lange diese an der Druckwaage das Druckgleichgewicht zwischen dem Versorgungsdruck des Verbrauchers und deren Lastdruck, zuzüglich des an der Druckwaage wirkenden Federdruckes, aufrechterhalten kann. Erfordert der Verbraucher einen Volumenstrom über dem vollen Förderstrom der Konstantpumpe, so dass dieses Druckgleichgewicht nicht aufrechterhalten bleibt, dann verschiebt die Feder den Ventilkolben der Druckwaage in Regelpositionen, bei denen eine Verbindung zwischen der Zusatzpumpe und dem Versorgungsanschluss des Verbrauchers gebildet ist.In this arrangement, the consumer is normally supplied by the fixed displacement pump as long as it can maintain the pressure balance between the supply pressure of the consumer and its load pressure, plus the spring pressure acting on the pressure compensator. If the consumer requires a volume flow above the full flow rate of the fixed displacement pump, so that this pressure equilibrium is not maintained, then the spring moves the valve piston of the pressure compensator into control positions in which a connection is established between the additional pump and the supply connection of the consumer.

Es ist ferner vorgesehen, dass das System neben der Konstantpumpe eine Zusatzpumpe aufweist und dass eine Ventilanordnung vorgesehen ist, mittels deren in Abhängigkeit von einem Lastdruck des betreffenden Verbrauchers, bei dem dessen Versorgungsbedarf den vollen Förderstrom der Konstantpumpe übersteigt, die Zusatzpumpe dem Verbraucher zuschaltbar ist. Dadurch entfällt die Notwendigkeit, aus Sicherheitsgründen die Konstantpumpe auf möglicherweise im Betrieb auftretende Spitzenwerte des Lastdruckes auszulegen, d.h. sozusagen zu "überdimensionieren". Vielmehr kann in vorteilhafter Weise die Konstantpumpe auf sozusagen normale Lastdrücke, wie sie im Betrieb während überwiegender Betriebsphasen auftreten, ausgelegt werden, weil bei einer in Extremfällen drohenden Unterversorgung ein Volumenstrom aus der Zusatzpumpe zugeschaltet wird.It is also provided that the system has an additional pump in addition to the fixed displacement pump and that a valve arrangement is provided by means of which the additional pump can be switched on to the consumer as a function of a load pressure of the consumer in question, at which the supply requirement exceeds the full flow rate of the fixed displacement pump. This eliminates the need, for safety reasons, to design the fixed displacement pump for peak values of the load pressure that may occur during operation, ie to "oversize" it, so to speak. Rather, the fixed displacement pump can advantageously be designed for normal load pressures, so to speak, as they occur during operation during predominant operating phases, because in extreme cases there is a threat of undersupply, a volume flow from the additional pump is switched on.

Aufgrund der durch die bedarfsweise erfolgende Zusatzversorgung erreichten Betriebssicherheit kann das erfindungsgemäße Hydrauliksystem mit besonderem Vorteil zur Versorgung einer hydraulisch betätigbaren Lenkung eines Fahrzeugs vorgesehen sein.Due to the operational reliability achieved by the additional supply that takes place as required, the hydraulic system according to the invention can be provided with particular advantage for supplying a hydraulically actuated steering system of a vehicle.

Bei dem erfindungsgemäßen Hydrauliksystem kann außer der Lenkung, die als Verbraucher erster Priorität bei Bedarf durch Volumenströme aus Konstantpumpe und Zusatzpumpe versorgbar ist, mindestens ein weiterer Verbraucher minderer Priorität dem System zugeordnet sein, wobei ein solcher Verbraucher minderer Priorität entweder durch einen Volumenstrom aus Zusatzpumpe oder Konstantpumpe versorgbar sein kann.In the hydraulic system according to the invention, in addition to the steering, which can be supplied as a first priority consumer if required by volume flows from the fixed displacement pump and auxiliary pump, at least one further consumer of lower priority can be assigned to the system, with such a consumer of lower priority either by a volume flow from the auxiliary pump or constant pump can be supplied.

In besonders vorteilhafter Weise kann eine Zusatzpumpe in Form einer Regelpumpe vorgesehen sein, wobei mindestens einer der Verbraucher minderer Priorität für die Versorgung durch die Regelpumpe mit dieser verbunden sein kann.In a particularly advantageous manner, an additional pump in the form of a regulating pump can be provided, with at least one of the consumers of lower priority for the supply by the regulating pump being able to be connected to the latter.

Bei besonders vorteilhaften Ausführungsbeispielen kann die Anordnung so getroffen sein, dass der Lastdruck der Lenkung und der höchste Lastdruck der mit der Regelpumpe verbundenen Verbraucher minderer Priorität an einem Wechselventil anstehen, das den jeweils dominanten Lastdruck dem Regler der Regelpumpe zuführt. Mittels der Regelpumpe, vorzugsweise in Form einer volumenstromgeregelten Kolbenpumpe, ist dadurch der Versorgungsdruck für jeweilige Verbraucher minderer Priorität auf das momentane Druckniveau des Verbrauchers mit dem höchsten Lastdruck einstellbar. Der momentane Druck der Regelpumpe kann dabei wesentlich über dem erforderlichen Versorgungsdruck der Lenkung liegen. Da jedoch bei Regelpositionen der Druckwaage, bei denen die Regelpumpe als Zusatzpumpe an der Versorgung der Lenkung beteiligt ist, der Druck der Regelpumpe auch an der Druckwaage wirksam ist und der durch den Lastdruck der Lenkung und den Federdruck gebildeten Verschiebekraft entgegenwirkt, wird die Lenkung wegen der Individual-Druckwaagenfunktion nur mit dem erforderlichen Lenkdruck versorgt.In particularly advantageous embodiments, the arrangement can be made such that the load pressure of the steering and the highest load pressure of the consumers connected to the control pump with lower priority are present at a shuttle valve that supplies the respective dominant load pressure to the controller of the control pump. By means of the regulating pump, preferably in the form of a volume flow-regulated piston pump, the supply pressure for the respective consumer with lower priority can be adjusted to the current pressure level of the consumer with the highest load pressure. The current pressure of the control pump can be significantly higher than the required supply pressure of the steering. Since, however, in control positions of the pressure compensator, in which the control pump is involved as an additional pump in the supply of the steering, the pressure of the control pump is also effective on the pressure compensator and that of the load pressure of the steering and counteracts the displacement force formed by the spring pressure, the steering is only supplied with the required steering pressure due to the individual pressure compensator function.

In der von der Druckwaage zum Tank führenden Leitung kann ein Verbraucher minderer Priorität, beispielsweise in Form eines Kühlers, angeordnet sein.A lower priority consumer, for example in the form of a cooler, can be arranged in the line leading from the pressure compensator to the tank.

Nachstehend ist die Erfindung anhand eines in der Zeichnung dargestellten Ausführungsbeispiels im Einzelnen erläutert. Es zeigen:

  • Fig. 1 bis 3 Symboldarstellungen der Schaltung eines Ausführungsbeispiels des erfindungsgemäßen Hydrauliksystems, wobei in den Figuren jeweils unterschiedliche Regelpositionen einer Druckwaage dargestellt sind.
The invention is explained in detail below on the basis of an exemplary embodiment shown in the drawing. Show it:
  • Figs. 1 to 3 Symbolic representations of the circuit of an exemplary embodiment of the hydraulic system according to the invention, different control positions of a pressure compensator being shown in each of the figures.

In der Zeichnung ist die Erfindung anhand eines Beispiels erläutert, bei dem die hydraulisch betätigbare Lenkung 1 eines Fahrzeugs als Verbraucher erster Priorität mit hydraulischem Druck versorgt werden soll. Das System weist hierfür eine Konstantpumpe 3 sowie eine Regelpumpe 5 auf. Beim vorliegenden Beispiel ist die Konstantpumpe 3 durch eine Zahnradpumpe gebildet, und als Regelpumpe 5 ist eine volumenstromgeregelte Kolbenpumpe vorgesehen. Der druckseitige Ausgang der Konstantpumpe 3 ist über eine Versorgungsleitung 7 mit dem Versorgungsanschluss PL der Lenkung 1 verbunden. Diese weist außer dem Versorgungsanschluss PL einen Load-Sensing-Anschluss LS auf, der den jeweiligen Lastdruck führt. Ein Tankanschluss T der Lenkung 1 ist mit Tank verbunden. Die Regelpumpe 5 ist an ihrem druckseitigen Anschluss über eine Leitung 9 mit einer Individual-Druckwaage 11 verbunden, bei der es sich beim vorliegenden Beispiel um ein 4/3-Wege-Ventil mit zwei Steuerkanten und Stetigfunktion handelt. Die Druckwaage 11 weist zwei zuströmseitige Anschlüsse auf, an deren einem Anschluss 13 die Ausgangsseite der Konstantpumpe 3 sowie eine Steuerleitung 15 angeschlossen sind, deren Steuerdruck, der dem Druck der Konstantpumpe 3 und damit dem Druck am Versorgungsanschluss PL der Lenkung 1 entspricht, an einer Seite des Ventilkolbens der Druckwaage 11 angreift. Der zweite zuströmseitige Anschluss 17 der Druckwaage 11 ist mit der Leitung 9 am druckseitigen Ausgang der Regelpumpe 5 verbunden. Ein erster abströmseitiger Anschluss 19 ist über ein Rückschlagventil 21 mit der Versorgungsleitung 7 und damit mit dem Versorgungsanschluss PL der Lenkung 1 in Verbindung. Am zweiten abströmseitigen Anschluss 22 der Druckwaage 11 ist eine Leitung 24 angeschlossen, die über einen Kühler zum Tank führt.In the drawing, the invention is explained using an example in which the hydraulically actuated steering system 1 of a vehicle is to be supplied with hydraulic pressure as a first priority consumer. The system has a fixed displacement pump 3 and a control pump 5 for this purpose. In the present example, the fixed displacement pump 3 is formed by a gear pump, and a volume flow-controlled piston pump is provided as the control pump 5. The pressure-side output of the fixed displacement pump 3 is connected to the supply connection PL of the steering system 1 via a supply line 7. In addition to the supply connection PL, this has a load-sensing connection LS, which carries the respective load pressure. A tank connection T of the steering system 1 is connected to the tank. The regulating pump 5 is connected at its pressure-side connection via a line 9 to an individual pressure compensator 11, which in the present example is a 4/3-way valve with two control edges and a continuous function. The pressure compensator 11 has two inflow-side connections, at one of which Connection 13, the output side of the fixed displacement pump 3 and a control line 15 are connected, the control pressure of which, which corresponds to the pressure of the fixed displacement pump 3 and thus the pressure at the supply connection PL of the steering system 1, acts on one side of the valve piston of the pressure compensator 11. The second connection 17 on the inflow side of the pressure compensator 11 is connected to the line 9 at the outlet of the regulating pump 5 on the pressure side. A first downstream connection 19 is connected via a check valve 21 to the supply line 7 and thus to the supply connection PL of the steering system 1. A line 24 is connected to the second downstream connection 22 of the pressure compensator 11 and leads to the tank via a cooler.

Das der Steuerleitung 15 gegenüberliegende Ende des Ventilkolbens der Druckwaage 11 ist vom Lastdruck der Lenkung 1, der vom Load-Sensing-Anschluss LS her über eine Steuerleitung 25 zugeführt wird, sowie vom Druck einer Feder 23 beaufschlagt. Die den Lastdruck führende Steuerleitung 25 ist über eine Verbindungsleitung 27 auch mit einer Seite eines Wechselventils 29 verbunden, an dem andererseits eine Lastdruckleitung 31 angeschlossen ist. Diese führt den Lastdruck weiterer, dem System zugeordneter Verbraucher, die dem System zugeordnet sind und von der Regelpumpe 5 über eine an deren druckseitigem Ausgang angeschlossene Druckleitung 33 versorgt sind. Bei einem Hydrauliksystem eines Fahrzeugs kann es sich bei den weiteren Verbrauchern beispielsweise um eine Niveauregelung, Federung/Dämpfung, um eine Bremseinrichtung oder dergleichen handeln. Das Wechselventil 29 vergleicht den an der Verbindungsleitung 27 anstehenden Lastdruck der Lenkung 1 mit dem höchsten Lastdruck der weiteren Verbraucher, der an der Lastdruckleitung 31 ansteht, und meldet den jeweils dominanten Druck zum Regleranschluss 35 der Regelpumpe 5. Diese regelt den Versorgungsdruck in der Versorgungsleitung 9, der am Anschluss 7 der Druckwaage 11 ansteht, auf zumindest den Lastdruck der Lenkung 1 plus Regeldruckdifferenz des Reglers der Regelpumpe 5.The end of the valve piston of the pressure compensator 11 opposite the control line 15 is acted upon by the load pressure of the steering 1, which is supplied from the load-sensing connection LS via a control line 25, and by the pressure of a spring 23. The control line 25 carrying the load pressure is also connected via a connecting line 27 to one side of a shuttle valve 29 to which a load pressure line 31 is connected on the other hand. This guides the load pressure of further consumers assigned to the system, which are assigned to the system and are supplied by the regulating pump 5 via a pressure line 33 connected to its outlet on the pressure side. In the case of a hydraulic system of a vehicle, the additional consumers can be, for example, level control, suspension / damping, a braking device or the like. The shuttle valve 29 compares the load pressure of the steering 1 on the connecting line 27 with the highest load pressure of the other consumers on the load pressure line 31 and reports the dominant pressure to the regulator connection 35 of the regulating pump 5. This regulates the supply pressure in the supply line 9 , which is present at the connection 7 of the pressure compensator 11, to at least the load pressure of the steering 1 plus the control pressure difference of the controller of the control pump 5.

Wird die Lenkung hinreichend aus der Konstantpumpe 3 versorgt, steht die Druckwaage 11 auf den in den Fig. 1 und 2 gezeigten Regelpositionen. Dabei entspricht die Position von Fig. 1 dem Betriebszustand bei einem Lastdruck der Lenkung 1, bei dem überschüssiger Volumenstrom der Konstantpumpe 3 über den zuströmseitigen Anschluss 13 und den abströmseitigen Anschluss 22 der Druckwaage 1 zum Tank hin abströmt. Die Verbindung zur Regelpumpe 5 über die Versorgungsleitung 9 ist gesperrt. Die Fig. 2 zeigt den Betriebszustand, bei dem die Verbindung zur Regelpumpe 5 weiterhin gesperrt ist, Druckgleichgewicht an der Druckwaage 11 herrscht und die Lenkung 1 lediglich von der Konstantpumpe 3 über die Versorgungsleitung 7 versorgt wird. Schließlich zeigt die Fig. 3 den Betriebszustand, bei dem eine Versorgung ausschließlich aus der Konstantpumpe 3 zur Unterversorgung der Lenkung 1 führen würde. Bei dem hierbei gegebenen Lastdruck der Lenkung 1, der über die Steuerleitung 25 am Ventilkolben der Druckwaage 11 zusammen mit dem Druck der Feder 23 wirksam ist, ist der Ventilkolben gegen die schwächere Wirkung des Druckes der Konstantpumpe 3, der über die Steuerleitung 15 zugeführt wird, nach links in die Regelposition von Fig. 3 verschoben. Hierbei ist die Regelpumpe 5 über die Versorgungsleitung 9 sowie den abströmseitigen Anschluss 19 der Druckwaage 11 und über das Rückschlagventil 21 mit dem Versorgungsanschluss PL der Lenkung 1 verbunden.If the steering is sufficiently supplied from the fixed displacement pump 3, the pressure compensator 11 is set to the Fig. 1 and 2 control positions shown. The position corresponds to Fig. 1 the operating state at a load pressure of the steering system 1, in which the excess volume flow of the fixed displacement pump 3 flows off via the inflow-side connection 13 and the outflow-side connection 22 of the pressure compensator 1 to the tank. The connection to the regulating pump 5 via the supply line 9 is blocked. the Fig. 2 shows the operating state in which the connection to the regulating pump 5 is still blocked, there is pressure equilibrium at the pressure compensator 11 and the steering system 1 is only supplied by the fixed displacement pump 3 via the supply line 7. Finally shows the Fig. 3 the operating state in which a supply exclusively from the fixed displacement pump 3 would lead to an undersupply of the steering system 1. At the given load pressure of the steering 1, which is effective via the control line 25 on the valve piston of the pressure compensator 11 together with the pressure of the spring 23, the valve piston is against the weaker effect of the pressure of the constant pump 3, which is supplied via the control line 15, to the left in the normal position of Fig. 3 postponed. Here, the regulating pump 5 is connected to the supply connection PL of the steering system 1 via the supply line 9 and the downstream connection 19 of the pressure compensator 11 and via the check valve 21.

Bei entsprechend hohen Lastdrücken weiterer Verbraucher, die dem System zugehörig sind und über die Druckleitung 33 von der Regelpumpe 5 versorgbar sind, kann die Regelpumpe 5 auf einen Ausgangsdruck geregelt werden, der wesentlich über dem erforderlichen Versorgungsdruck der Lenkung 1 liegt. Da jedoch bei der in Fig. 3 gezeigten Regelposition der Ausgangsdruck der Regelpumpe 5 über die Versorgungsleitung 9, die Anschlüsse 17 und 19 sowie das Rückschlagventil 21 und die Versorgungsleitung 7 auch am zuströmseitigen Anschluss 13 ansteht und somit über die Steuerleitung 15 auch am Ventilkolben der Druckwaage 11 wirksam ist, wird die Lenkung 1 unabhängig vom Pumpendruck der Regelpumpe 5 nur mit dem Versorgungsdruck versorgt, der dem jeweils herrschenden Lastdruck der Lenkung 1 plus dem Druck der Feder 23 entspricht.At correspondingly high load pressures of other consumers that are part of the system and can be supplied by the regulating pump 5 via the pressure line 33, the regulating pump 5 can be regulated to an output pressure which is significantly above the required supply pressure of the steering system 1. However, since the in Fig. 3 The control position shown, the output pressure of the control pump 5 via the supply line 9, the connections 17 and 19 as well as the check valve 21 and the supply line 7 is also present at the inflow-side connection 13 and is therefore also effective on the valve piston of the pressure compensator 11 via the control line 15, the steering system 1 is only supplied with the supply pressure that corresponds to the prevailing load pressure of the steering system 1 plus the pressure of the spring 23, regardless of the pump pressure of the regulating pump 5.

Claims (7)

  1. Hydraulic system for reliably supplying pressure to at least one consumer (1), having a consumer (1), a fixed-displacement pump (3) which provides a constant flow rate for the consumer (1), a booster pump (5) and a valve arrangement (11) by means of which the booster pump (5) can be connected to the consumer (1) as a function of a load pressure (LS) of the consumer (1), at which load pressure its supply requirement exceeds the full flow rate of the fixed-displacement pump (3), wherein the valve arrangement has a pressure compensator (11), wherein the pressure of the fixed-displacement pump (3) and thus the pressure at the supply connection (PL) of the consumer (1), on the one hand, and the load pressure (LS) of the consumer (1) plus a spring pressure (23), on the other hand, are present at the valve piston of the pressure compensator (11) and wherein the booster pump (5) is connected via the pressure compensator (11) to the supply connection (PL) of the consumer (1) at regulating positions of the pressure compensator (11), at which the pressure of the fixed-displacement pump (3) is lower than the load pressure (LS) plus the spring pressure (23), characterised in that the pressure compensator is provided in the form of a 4/3-way valve (11), wherein the fixed-displacement pump (3) is connected to one of its inlet-side connections (13), the variable-displacement pump (5) is connected to the other inlet-side connection (17), the supply connection (PL) of the consumer (1) is connected to an outlet-side connection (19) and a line (24) leading to the tank is connected to the other outlet-side connection (22).
  2. Hydraulic system according to claim 1, characterised in that it comprises a plurality of consumers and that it is provided to supply a hydraulically operable steering system (1) of a vehicle as a first priority consumer.
  3. Hydraulic system according to claim 2, characterised in that, apart from the steering system (1), which as a first priority consumer can be supplied as needed by volume flows from a fixed-displacement pump (3) and a booster pump (5), the system comprises at least one further lower priority consumer which can be supplied by a volume flow from a booster pump (5) or a fixed-displacement pump (3)
  4. Hydraulic system according to one of the preceding claims, characterised in that the booster pump is provided in the form of a variable-displacement pump (5).
  5. Hydraulic system according to claims 3 and 4, characterised in that at least one of the lower priority consumers is connected to the variable-displacement pump (5) for being supplied thereby.
  6. Hydraulic system according to claim 5, characterised in that the load pressure (LS) of the steering system (1) and the highest load pressure of the lower priority consumer connected to the variable-displacement pump (5) are present at a shuttle valve (29) which supplies the dominant load pressure in each case to the controller (35) of the variable-displacement pump (5).
  7. Hydraulic system according to one of the preceding claims, characterised in that a lower priority consumer, for example in the form of a cooler, is arranged in the line (24) leading from the pressure compensator (11) to the tank.
EP13001739.5A 2012-06-08 2013-04-05 Hydraulic system for the reliable pressure supply to at least one consumer Active EP2672125B1 (en)

Applications Claiming Priority (1)

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DE102012011400A DE102012011400A1 (en) 2012-06-08 2012-06-08 Hydraulic system for safe pressure supply of at least one consumer

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EP2672125A2 EP2672125A2 (en) 2013-12-11
EP2672125A3 EP2672125A3 (en) 2017-12-27
EP2672125B1 true EP2672125B1 (en) 2021-09-01

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015109508A1 (en) 2015-06-15 2016-12-15 Robert Bosch Automotive Steering Gmbh Hydraulic pump arrangement, in particular for a steering system of a motor vehicle
CN106836337B (en) * 2017-03-30 2022-09-20 徐州徐工筑路机械有限公司 Land leveler variable hydraulic system
DE102017004634A1 (en) * 2017-05-15 2018-11-15 Hydac Systems & Services Gmbh Control device for supplying at least one hydraulic consumer
CN112922914A (en) * 2021-01-12 2021-06-08 盾构及掘进技术国家重点实验室 High-efficiency precise synchronous lifting hydraulic control system for segment assembly of shield tunneling machine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3608469A1 (en) * 1986-03-14 1987-10-01 Bosch Gmbh Robert HYDRAULIC SYSTEM
DE4129508C2 (en) * 1991-09-05 1994-12-15 Rexroth Mannesmann Gmbh Valve arrangement for supplying a consumer from two pressure medium sources
US5918558A (en) * 1997-12-01 1999-07-06 Case Corporation Dual-pump, flow-isolated hydraulic circuit for an agricultural tractor
AT3427U1 (en) * 1998-09-25 2000-03-27 Steyr Daimler Puch Ag HYDRAULIC SYSTEM FOR ARMED TRACTORS AND SELF-DRIVING WORKING MACHINES
DE10315496A1 (en) * 2003-04-04 2004-10-21 Linde Ag Hydraulic system for a battery-operated industrial truck has two hydraulic pumps, the second pump being used for additional supply to a lifting mechanism

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EP2672125A3 (en) 2017-12-27
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