EP0205925A2 - Control device for hydraulic power equipment - Google Patents

Control device for hydraulic power equipment Download PDF

Info

Publication number
EP0205925A2
EP0205925A2 EP86106864A EP86106864A EP0205925A2 EP 0205925 A2 EP0205925 A2 EP 0205925A2 EP 86106864 A EP86106864 A EP 86106864A EP 86106864 A EP86106864 A EP 86106864A EP 0205925 A2 EP0205925 A2 EP 0205925A2
Authority
EP
European Patent Office
Prior art keywords
pump
valve
control valve
electrically actuated
setpoint
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP86106864A
Other languages
German (de)
French (fr)
Other versions
EP0205925A3 (en
EP0205925B1 (en
Inventor
Erich Dipl.-Ing. Eckhardt
Gerhard Dipl.-Ing. Nonnenmacher
Roman Ing. Romes
Franz Dipl.-Ing.(Fh) Schwede
Dieter Dipl.-Ing. Weigle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0205925A2 publication Critical patent/EP0205925A2/en
Publication of EP0205925A3 publication Critical patent/EP0205925A3/en
Application granted granted Critical
Publication of EP0205925B1 publication Critical patent/EP0205925B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/087—Control strategy, e.g. with block diagram

Definitions

  • the invention relates to a control device for hydraulic machines according to the preamble of the main claim.
  • Such machines are usually controlled with the aid of directional control valves which, in addition to the neutral position and the maximum working position, have a fine control range in which only a part of the pump delivery flow is directed to the consumer (working cylinder, hydraulic motor).
  • the pump can be designed as a constant pump or variable pump. In such hydraulic circuits, throttling losses inevitably occur in the neutral position (circulating pressure at maximum flow) and in the fine control range (outflow of unused hydraulic fluid), which worsens the energy balance of the system.
  • control device with the characterizing features of the main claim has the advantage that it is very simple and allows to work with the least losses, d. that is, always adjust the pump so that it only provides the flow required by the consumers.
  • 10 is an adjustable pump which draws pressure medium from a container and displaces it into a delivery line 12.
  • the delivery line leads to a 4/3-way valve 13 with proportional behavior, which can be actuated by electromagnets 14, 15.
  • Two lines 16, 17 lead from the directional control valve to the pressure chambers 18, 19 of a double-acting working cylinder 20.
  • the actuator 22 of the adjustable pump 10 is actuated by two actuating pistons 23, 24 pressurized by pressure medium, of which the one with the smaller diameter 24 is pressurized via a line 25 connected to the delivery line.
  • a line 26 leads from the larger area piston 23 to a 3/3-way valve 27 with proportional behavior; it is actuated by an electromagnet 28 against the force of a control spring 21, which is supported on the actuating piston 23.
  • a line 30 leads from the directional control valve 27 to the delivery line 12 on the one hand, and a line 31 to the container 11 on the other hand.
  • the control of the directional control valves 13, 27 takes place via an adjusting device 32 designed as a setpoint device with an actuating lever 32 ', the angular position of which is converted into a proportional electrical signal, e.g. B. by a setpoint transmitter 33 designed as a rotary potentiometer.
  • the setpoint signals of the electrical setpoint generator thus formed lead via two lines 35, 36 to the electromagnets 14, 15 of the directional control valve 13, and from a summing point 38 and its amplifier 44 a line 39 leads to the electromagnet 28 of the directional control valve 27.
  • the control lever 32 'of the setpoint generator can be pivoted to both sides (-a; + ct) - and generates and sends corresponding setpoint signals to the directional control valves.
  • power amplifiers 42, 43 are arranged which supply the magnetic current.
  • the pump 10 is driven by an internal combustion engine 48.
  • the electrical setpoint generator 33 in addition to the position signal for the directional control valve 13, a position signal for the directional control valve 27 and thus for the pump 10 is obtained, which in this exemplary embodiment is designed such that the adjustment of the pump is proportional to the adjustment of the directional control valve 13.
  • the setpoint for the pump delivery rate and the actuation of the working cylinder 20 is predetermined via the setting lever 32 for the electrical setpoint generator 33.
  • an additional summing point 50 with amplifier 50 ' is also provided in line 39, to which a signal is supplied which causes the Adjustment of the pump relative to the adjustment of the directional control valve 13 has an approximately constant flow, ie the pump is adjusted earlier than the directional control valve 13.
  • the speed of the internal combustion engine 48 is also included in the control circuit.
  • An electronic divider 52 is inserted into line 39, and the speed of the internal combustion engine is entered via line 53 as a divisor.
  • the power amplifier 45 which supplies the magnetic current, is located in line 39 behind the divider.
  • Figure 4 follows that of Figure 1, but with the difference that here a second cylinder 55 with associated 4/3-way proportional valve 56 is provided, and a second actuator 57 with lever 57 'and elec trical Setpoint generator 58. Details are - so far not readily understandable - only taken into account insofar as a line 59 leads from the actuating device 57 to a second summing point 60 of the line 39, so that also from the actuation of the second consumer 55 Signal is given to the directional control valve 27, whereby the pump flow is increased according to this additional need.
  • a combination of the last-mentioned exemplary embodiment with that according to FIG. 3 represents the exemplary embodiment according to FIG. 5, where the internal combustion engine 48 is again included in the control circuit. Their load state is compared in an electronic control unit with a target value for the maximum load. Two lines 63, 64 lead from the control device 62 to electrical limiters 65 and 66, which can reduce the setpoint signals of the actuating devices 32, 57. When a predetermined limit is reached, e.g. B. the power limit of the internal combustion engine, the setpoints for the adjustment of the directional control valves are reduced according to a preprogrammed priority plan. The pump 10 is then reset as in the case of the previous exemplary embodiments.
  • a predetermined limit e.g. B. the power limit of the internal combustion engine
  • the device according to the invention also has the advantage that an energy saving is achieved with conventional directional valves, which otherwise can only be achieved with load-sensing technology. Furthermore, the device according to the invention also offers intervention options for higher-level signals that far exceed previously known limit load regulations or power regulations. As can be seen from the above, the device makes use of the consideration of electrically adjusting the control valves to avoid long rods and hydraulic lines; the same applies to the pump.

Abstract

The control device has a proportional directional valve (13) for a consuming device (20) as well as a proportionally working control valve (27) for an adjustable pump (10). The valves are adjusted in proportion to an input desired value by an electronic regulating device (32). In this way, a simple adjusting device is obtained which avoids long linkages and hydraulic lines. Through a simple auxiliary member, it is possible to give the pump adjustment an advance over the consuming device. In addition, it is possible to feed the speed of the power equipment into the control device, as a result of which the saving in energy becomes particularly great. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Steuereinrichtung für hydraulische Arbeitsmaschinen nach der Gattung des Hauptanspruchs. Die Steuerung derartiger Arbeitsmaschinen erfolgt üblicherweise mit Hilfe von Wegeventilen, die außer der Neutralstellung und der maximalen Arbeitsstellung einen Feinsteuerbereich haben, in dem nur ein Teil des Pumpenförderstroms zum Verbraucher (Arbeitszylinder, Hydromotor) geleitet wird. Die Pumpe kann dabei als Konstantpumpe oder Verstellpumpe ausgebildet sein. In solchen Hydraulikkreisen entstehen zwangsläufig in der Neutralstellung (Umlaufdruck bei maximalem Förderstrom) und im Feinsteuerbereich (Abströmen nicht genutzter Hydraulikflüssigkeit) Drosselverluste, die die Energiebilanz der Anlage verschlechtem.The invention relates to a control device for hydraulic machines according to the preamble of the main claim. Such machines are usually controlled with the aid of directional control valves which, in addition to the neutral position and the maximum working position, have a fine control range in which only a part of the pump delivery flow is directed to the consumer (working cylinder, hydraulic motor). The pump can be designed as a constant pump or variable pump. In such hydraulic circuits, throttling losses inevitably occur in the neutral position (circulating pressure at maximum flow) and in the fine control range (outflow of unused hydraulic fluid), which worsens the energy balance of the system.

Um solche Verluste zu vermeiden, ist es bekannt, sogenannte load-sensing-Systeme einzusetzen, die jedoch eine besondere Gattung von Regelventilen, Steuerleitungen und speziellen Pumpensteuerungen erfordern. Der Aufwand für die Leistungsbegrenzung ist hoch. Trotzdem sind solche Wegeventile nicht frei von Drosselverlusten, vor allem bei hohem Durchfluß.In order to avoid such losses, it is known to use so-called load-sensing systems, which, however, require a special type of control valves, control lines and special pump controls. The effort to limit performance is high. Nevertheless, such directional control valves are not free from throttling losses, especially at high flow rates.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Steuereinrichtung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß sie sehr einfach ist und es erlaubt, mit geringsten Verlusten zu arbeiten, d. h., die Pumpe stets so einzustellen, daß sie nur gerade den von den Verbrauchern benötigten Förderstrom erbringt.The control device according to the invention with the characterizing features of the main claim has the advantage that it is very simple and allows to work with the least losses, d. that is, always adjust the pump so that it only provides the flow required by the consumers.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind Weiterbildungen der im Hauptanspruch angegebenen Merkmale möglich.The measures listed in the subclaims allow further developments of the features specified in the main claim.

Zeichnungdrawing

Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Die Figuren zeigen Steuereinrichtungen für hydraulische Arbeitsmaschinen in schematischer Darstellung.Several embodiments of the invention are shown in the drawing and explained in more detail in the following description. The figures show control devices for hydraulic machines in a schematic representation.

Beschreibung der ErfindungsbeispieleDescription of the invention examples

In Figur 1 ist mit 10 eine verstellbare Pumpe bezeichnet, die Druckmittel aus einem Behälterl ansaugt und dieses in eine Förderleitung 12 verdrängt. Die Förderleitung führt zu einem 4/3-Wegeventil 13 mit Proportionalverhalten, das durch Elektromagnete 14, 15 betätigbar ist. Vom Wegeventil führen zwei Leitungen 16, 17 zu den Druckräumen 18, 19 eines doppeltwirkenden Arbeitszylinders 20.In FIG. 1, 10 is an adjustable pump which draws pressure medium from a container and displaces it into a delivery line 12. The delivery line leads to a 4/3-way valve 13 with proportional behavior, which can be actuated by electromagnets 14, 15. Two lines 16, 17 lead from the directional control valve to the pressure chambers 18, 19 of a double-acting working cylinder 20.

Das Stellglied 22 der verstellbaren Pumpe 10 wird durch zwei druckmittelbeaufschlagte Stellkolben 23, 24 betätigt, von denen derjenige mit dem kleineren Durchmesser 24 über eine an die Förderleitung angeschlossene Leitung 25 mit Druck beaufschlagt wird. Vom flächengrößeren Kolben 23 führt eine Leitung 26 zu einem 3/3-Wegeventil 27 mit proportionalem Verhalten; es wird über einen Elektromagneten 28 entgegen der Kraft einer Regelfeder 21 betätigt, welche sich am Stellkolben 23 abstützt. Vom Wegeventil 27 führt einerseits eine Leitung 30 zur Förderleitung 12, andererseits eine Leitung 31 zum Behälter 11.The actuator 22 of the adjustable pump 10 is actuated by two actuating pistons 23, 24 pressurized by pressure medium, of which the one with the smaller diameter 24 is pressurized via a line 25 connected to the delivery line. A line 26 leads from the larger area piston 23 to a 3/3-way valve 27 with proportional behavior; it is actuated by an electromagnet 28 against the force of a control spring 21, which is supported on the actuating piston 23. A line 30 leads from the directional control valve 27 to the delivery line 12 on the one hand, and a line 31 to the container 11 on the other hand.

Die Ansteuerung der Wegeventile 13, 27 erfolgt über eine als Sollwertgeber ausgebildete Stelleinrichtung 32 mit Stellhebel 32', dessen Winkelstellung in ein proportionales elektrisches Signal umgeformt wird, z. B. durch einen als Drehpotentiometer ausgebildeten Sollwertgeber 33. Die so gebildeten Sollwertsignale des elektrischen Sollwertgebers führen über zwei Leitungen 35, 36 zu den Elektromagneten 14, 15 des Wegeventils 13, und von einem Summierpunkt 38 und dessen Verstärker 44 führt eine Leitung 39 zum Elektromagneten 28 des Wegeventils 27. Der Stellhebel 32' des Sollwertgebers ist nach beiden Seiten (-a; + ct ) - schwenkbar und erzeugt und schickt entsprechende Sollwertsignale zu den Wegeventilen. In den Leitungen 35, 36 sind Leistungsverstärker 42, 43 angeordnet, die den Magnetstrom liefem. In der Leitung 39 befindet sich ebenfalls ein Leistungsverstärker 45.The control of the directional control valves 13, 27 takes place via an adjusting device 32 designed as a setpoint device with an actuating lever 32 ', the angular position of which is converted into a proportional electrical signal, e.g. B. by a setpoint transmitter 33 designed as a rotary potentiometer. The setpoint signals of the electrical setpoint generator thus formed lead via two lines 35, 36 to the electromagnets 14, 15 of the directional control valve 13, and from a summing point 38 and its amplifier 44 a line 39 leads to the electromagnet 28 of the directional control valve 27. The control lever 32 'of the setpoint generator can be pivoted to both sides (-a; + ct) - and generates and sends corresponding setpoint signals to the directional control valves. In the lines 35, 36, power amplifiers 42, 43 are arranged which supply the magnetic current. There is also a power amplifier 45 in line 39.

Die Pumpe 10 ist von einer Brennkraftmaschine 48 angetrieben. Mit dem elektrischen Sollwertgeber 33 wird zusätzlich zum Stellungssignal für das Wegeventil 13 auch ein Stellungssignal für das Wegeventil 27 und damit für die Pumpe 10 gewonnen, das in diesem Ausführungsbeispiel so ausgelegt ist, daß die Verstellung der Pumpe proportional zur Verstellung des Wegeventils 13 ist. Über den Stellhebel 32 wird dem elektrischen Sollwertgeber 33 der Sollwert für die Pumpenfördermenge und die Betätigung des Arbeitszylinders 20 vorgegeben.The pump 10 is driven by an internal combustion engine 48. With the electrical setpoint generator 33, in addition to the position signal for the directional control valve 13, a position signal for the directional control valve 27 and thus for the pump 10 is obtained, which in this exemplary embodiment is designed such that the adjustment of the pump is proportional to the adjustment of the directional control valve 13. The setpoint for the pump delivery rate and the actuation of the working cylinder 20 is predetermined via the setting lever 32 for the electrical setpoint generator 33.

Beim Ausführungsbeispiel nach Figur 2, das weitgehend demjenigen nach Figur 1 entspricht, ist in der Leitung 39 noch ein zusätzlicher Summierpunkt 50 mit Verstärker 50' vorgesehen, dem ein Signal zugeführt wird, welches bewirkt, daß die Verstellung der Pumpe gegenüber der Verstellung des Wegeventils 13 einen etwa konstanten Vorlauf besitzt, d. h. die Pumpe wird früher verstellt als das Wegeventil 13.In the exemplary embodiment according to FIG. 2, which largely corresponds to that according to FIG. 1, an additional summing point 50 with amplifier 50 'is also provided in line 39, to which a signal is supplied which causes the Adjustment of the pump relative to the adjustment of the directional control valve 13 has an approximately constant flow, ie the pump is adjusted earlier than the directional control valve 13.

Beim Ausführungsbeispiel nach Figur 3 ist auch die Drehzahl der Brennkraftmaschine 48 mit in den Steuerkreis einbezogen. In die Leitung 39 ist ein elektronisches Dividierglied 52 eingesetzt, dem über eine Leitung 53 als Divisor die Drehzahl der Brennkraftmaschine eingegeben wird. Außerdem befindet sich in der Leitung 39 hinter dem Dividierglied wieder der Leistungsverstärker 45, der den Magnetstrom liefert. Mit dieser Anordnung erreicht man, daß die Verstellung der Pumpe proportional zur Verstellung der Wegeventile erfolgt, dividiert durch die Drehzahl der Brennkraftmaschine; d. h. der Förderstrom bleibt unabhängig von der Drehzahl, weil z. B. bei langsam drehender Brennkraftmaschine die Pumpe weiter ausgestellt wird als bei hoher Drehzahl.In the exemplary embodiment according to FIG. 3, the speed of the internal combustion engine 48 is also included in the control circuit. An electronic divider 52 is inserted into line 39, and the speed of the internal combustion engine is entered via line 53 as a divisor. In addition, the power amplifier 45, which supplies the magnetic current, is located in line 39 behind the divider. With this arrangement it is achieved that the adjustment of the pump is proportional to the adjustment of the directional valves, divided by the speed of the internal combustion engine; d. H. the flow rate remains independent of the speed, because z. B. with a slowly rotating internal combustion engine, the pump is turned off more than at high speed.

Das Ausführungsbeispiel nach Figur 4 schließt sich an dasjenige nach Figur 1 an, jedoch mit dem Unterschied, daß hier ein zweiter Arbeitszylinder 55 mit zugehörigem 4/3-Wege-Proportionalventil 56 vorgesehen ist, sowie eine zweite Stelleinrichtung 57 mit Stellhebel 57' und elek trischem Sollwertgeber 58. Auf Einzelheiten ist -so weit nicht ohne weiteres verständlich -nur insoweit eingegangen, als von der Stelleinrichtung 57 eine Leitung 59 zu einem zweiten Summierpunkt 60 der Leitung 39 geführt ist, so daß also auch von der Betätigung des zweiten Verbrauchers 55 her ein Signal zum Wegeventil 27 gegeben wird, wodurch der Pumpenförderstrom entsprechend diesem Zusatzbedarf erhöht wird.The embodiment of Figure 4 follows that of Figure 1, but with the difference that here a second cylinder 55 with associated 4/3-way proportional valve 56 is provided, and a second actuator 57 with lever 57 'and elec trical Setpoint generator 58. Details are - so far not readily understandable - only taken into account insofar as a line 59 leads from the actuating device 57 to a second summing point 60 of the line 39, so that also from the actuation of the second consumer 55 Signal is given to the directional control valve 27, whereby the pump flow is increased according to this additional need.

Eine Kombination des zuletztgenannten Ausführungsbeispiels mit demjenigen nach Figur 3 stellt das Ausführungsbeispiel nach Figur 5 dar, wo also wieder die Brennkraftmaschine 48 in den Steuerkreis einbezogen ist. Deren Lastzustand wird in einem elektronischen Steuergerät mit einem Sollwert für die Maximallast verglichen. Vom Steuergerät 62 führen zwei Leitungen 63, 64 zu elektrischen Begrenzem 65 und 66, die die Sollwertsignale der Stelleinrichtungen 32, 57 verringern können. Beim Erreichen eines vorgegebenen Grenzwertes, z. B. der Leistungsgrenze der Brennkraftmaschine, werden nach einem vorprogrammierten Prioritätsplan die Sollwerte für die Verstellung der Wegeventile reduziert. Die Zurückstellung der Pumpe 10 erfolgt dann wie im Fall der vorherigen Ausführungsbeispiele.A combination of the last-mentioned exemplary embodiment with that according to FIG. 3 represents the exemplary embodiment according to FIG. 5, where the internal combustion engine 48 is again included in the control circuit. Their load state is compared in an electronic control unit with a target value for the maximum load. Two lines 63, 64 lead from the control device 62 to electrical limiters 65 and 66, which can reduce the setpoint signals of the actuating devices 32, 57. When a predetermined limit is reached, e.g. B. the power limit of the internal combustion engine, the setpoints for the adjustment of the directional control valves are reduced according to a preprogrammed priority plan. The pump 10 is then reset as in the case of the previous exemplary embodiments.

Die erfindungsgemäße Einrichtung hat darüber hinaus noch den Vorteil, daß mit herkömmlichen Wegeventilen eine Energieeinsparung erzielt wird, die sonst allenfalls mit load-sensing-Technik erreicht werden kann. Des weiteren bietet die erfindungsgemäße Einrichtung auch Eingriffsmöglichkeiten für übergeordnete Signale, die bisher bekannte Grenzlastregelungen oder Leistungsregelungen weit übertreffen. Die Einrichtung macht sich, wie aus Obigem zu erkennen ist -die Überlegung zunutze, zur Vermeidung langer Gestänge und Hydraulikleitungen die Verstellung der Regelventile elektrisch vorzunehmen; dasselbe gilt auch für die Pumpe.The device according to the invention also has the advantage that an energy saving is achieved with conventional directional valves, which otherwise can only be achieved with load-sensing technology. Furthermore, the device according to the invention also offers intervention options for higher-level signals that far exceed previously known limit load regulations or power regulations. As can be seen from the above, the device makes use of the consideration of electrically adjusting the control valves to avoid long rods and hydraulic lines; the same applies to the pump.

Claims (7)

1. Steuereinrichtung für hydraulische Arbeitsmaschinen mit einer verstellbaren Pumpe, deren druckbeaufschlagter Stellkolben für ihr Stellglied (22) über ein elektrisch betätigbares Steuerventil angesteuert wird und die Druckmittel über ein elektrisch betätigbares Wegeventil zu wenigstens einem Verbraucher steuert, dadurch gekennzeichnet, daß von mindestens einem von einem Stellhebel (32', 57') betätigbaren elektrischen Sollwertgeber (32, 57) sowohl das Wegeventil (13) wie auch das elektrisch betätigbare Steuerventil (27) ansteuerbar ist.1. Control device for hydraulic machines with an adjustable pump, the pressurized actuating piston for its actuator (22) is controlled via an electrically actuated control valve and controls the pressure medium via an electrically actuated directional valve to at least one consumer, characterized in that at least one of one Adjusting lever (32 ', 57') actuatable electrical setpoint device (32, 57), both the directional valve (13) and the electrically actuated control valve (27) can be controlled. 2. Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß sowohl das Wegeventil wie auch das Steuerventil proportional arbeitende Ventile sind.2. Device according to claim 1, characterized in that both the directional valve and the control valve are proportionally working valves. 3. Einrichtung nach einem der Ansprüche 1 und/oder 2, dadurch gekennzeichnet, daß der Pumpenförderstrom durch einen zusätzlichen Sollwert am Summierpunkt (50) gegenüber der Ventilauslenkung geringfügig voreilt.3. Device according to one of claims 1 and / or 2, characterized in that the pump flow is slightly advanced by an additional setpoint at the summing point (50) relative to the valve deflection. 4. Einrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß bei Auslenkung des elektrischen Sollwertgebers (32) dem der Pumpenauslenkung zugeordneten Steuerventil ein Signal zugeführt wird, das geringfügig größer ist als es der Auslenkung des Ventils (13) entspricht.4. Device according to one of claims 1 to 3, characterized in that when the electrical setpoint generator (32) is deflected, the control valve associated with the pump deflection is supplied with a signal which is slightly greater than the deflection of the valve (13). 5. Einrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß von der die Pumpe antreibenden Antriebsmaschine (48) ein Drehzahlsignal einem elektronischen Dividierglied (52) zugeleitet wird, das in den Betätigungskreis für das Steuerventil (27) eingreift.5. Device according to one of claims 1 to 4, characterized in that a speed signal is fed from the drive motor (48) driving an electronic divider (52) which engages in the actuating circuit for the control valve (27). 6. Einrichtung nach einem der Ansprüche 1 bis .4, dadurch gekennzeichnet, daß von der Pumpe mehrere Verbraucher versorgt werden, deren jedem ein elektrisch betätigbares Wegeventil zugeordnet ist.6. Device according to one of claims 1 to .4, characterized in that the pump supplies several consumers, each of which is assigned an electrically actuated directional valve. 7. Einrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, das von der Pumpe - (10) mehrere Verbraucher versorgt werden, deren jedem ein elektrisch betätigbares Wegeventil und elektronische Stelleinrichtungen zugeordnet sind, daß sich in beiden Verbraucherkreisen Begrenzer - (65, 66) befinden, welche mit einem elektronischen Steuergerät (62) in Verbindung stehen, dem das Lastsignal der Antriebsmaschine und ein Sollwert für die Maximallast eingespeist werden.7. Device according to one of claims 1 to 5, characterized in that the pump - (10) supplies several consumers, each of which is assigned an electrically actuated directional control valve and electronic actuating devices, that there are limiters in both consumer circuits - (65, 66 ) which are with an electronic Control unit (62) are connected to which the load signal of the drive machine and a setpoint for the maximum load are fed.
EP19860106864 1985-06-19 1986-05-21 Control device for hydraulic power equipment Expired - Lifetime EP0205925B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3521815 1985-06-19
DE19853521815 DE3521815A1 (en) 1985-06-19 1985-06-19 CONTROL DEVICE FOR HYDRAULIC WORKING MACHINES

Publications (3)

Publication Number Publication Date
EP0205925A2 true EP0205925A2 (en) 1986-12-30
EP0205925A3 EP0205925A3 (en) 1989-03-22
EP0205925B1 EP0205925B1 (en) 1992-02-05

Family

ID=6273575

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19860106864 Expired - Lifetime EP0205925B1 (en) 1985-06-19 1986-05-21 Control device for hydraulic power equipment

Country Status (2)

Country Link
EP (1) EP0205925B1 (en)
DE (2) DE3521815A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2648584A1 (en) * 1989-06-16 1990-12-21 Rexroth Sigma METHOD AND SYSTEM FOR REGULATING THE MIDDLE CURRENT THROUGH A LOAD, AND ELECTRIC REMOTE CONTROL DEVICE OF THE MANIPULATOR TYPE USING THE SAME
FR2650635A1 (en) * 1989-08-07 1991-02-08 Rexroth Sigma Method for operating at least one variable output pump in an electrohydraulic plant, and electrohydraulic plant implementing this method
EP0531746A1 (en) * 1991-09-07 1993-03-17 KIWA MASCHINENFABRIK GmbH Switching method and arrangement for controlling, in particular a crane installation
DE19545657A1 (en) * 1995-12-07 1997-06-12 Rexroth Mannesmann Gmbh Hydraulic valve arrangement with a pressure-controlled directional valve

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107917117A (en) * 2016-10-11 2018-04-17 张利 A kind of mechanical hydraulic servo cylinder

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1807171A1 (en) * 1968-11-06 1970-06-18 Bosch Gmbh Robert Device for the electro-hydraulic remote control of hydraulic directional control valves
GB1385099A (en) * 1972-08-25 1975-02-26 Coventry Climax Eng Ltd Industrial fork lift truck
EP0022104A2 (en) * 1979-06-15 1981-01-07 Akermans Verkstad AB Control system for limiting the power output of a hydraulic servomotor assembly
JPS5899501A (en) * 1981-12-03 1983-06-13 Ishikawajima Harima Heavy Ind Co Ltd Hydraulic pump control circuit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1807171A1 (en) * 1968-11-06 1970-06-18 Bosch Gmbh Robert Device for the electro-hydraulic remote control of hydraulic directional control valves
GB1385099A (en) * 1972-08-25 1975-02-26 Coventry Climax Eng Ltd Industrial fork lift truck
EP0022104A2 (en) * 1979-06-15 1981-01-07 Akermans Verkstad AB Control system for limiting the power output of a hydraulic servomotor assembly
JPS5899501A (en) * 1981-12-03 1983-06-13 Ishikawajima Harima Heavy Ind Co Ltd Hydraulic pump control circuit

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 7, Nr. 199 (M-240)[1344], 3. September 1983; & JP-A-58 099 501 (ISHIKAWAJIMA HARIMA JUKOGYO K.K.) 13-06-1983 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2648584A1 (en) * 1989-06-16 1990-12-21 Rexroth Sigma METHOD AND SYSTEM FOR REGULATING THE MIDDLE CURRENT THROUGH A LOAD, AND ELECTRIC REMOTE CONTROL DEVICE OF THE MANIPULATOR TYPE USING THE SAME
FR2650635A1 (en) * 1989-08-07 1991-02-08 Rexroth Sigma Method for operating at least one variable output pump in an electrohydraulic plant, and electrohydraulic plant implementing this method
EP0531746A1 (en) * 1991-09-07 1993-03-17 KIWA MASCHINENFABRIK GmbH Switching method and arrangement for controlling, in particular a crane installation
DE19545657A1 (en) * 1995-12-07 1997-06-12 Rexroth Mannesmann Gmbh Hydraulic valve arrangement with a pressure-controlled directional valve

Also Published As

Publication number Publication date
EP0205925A3 (en) 1989-03-22
DE3683805D1 (en) 1992-03-19
DE3521815A1 (en) 1987-01-02
EP0205925B1 (en) 1992-02-05

Similar Documents

Publication Publication Date Title
DE3546336C2 (en)
DE2651325C2 (en)
DE60319441T2 (en) Electronic control device based on speed for controlling a hydraulic circuit
EP1664551B1 (en) Control system and method for supplying pressure means to at least two hydraulic consumers
EP0164602B2 (en) Device for regulating the pressure and the capacity of a variable-capacity pump
DE2111359A1 (en) Control device for a hydraulic pump
EP0564939B1 (en) Hydraulic control system for several motors
DE3644736A1 (en) CONTROL ARRANGEMENT FOR AT LEAST TWO HYDRAULIC CONSUMERS SUPPLIED BY AT LEAST ONE PUMP
DE10000110B4 (en) Hydrostatic vehicle drive with control device and control device for hydrostatic drives
EP1288507B1 (en) Low-loss drive system for a hydraulic actuator
DE19906230B4 (en) Device and method for coupling a plurality of pumps
EP0203100B1 (en) Hydraulic installation
EP0275969A2 (en) Control device for a hydrostatic transmission for at least two users
EP0205925B1 (en) Control device for hydraulic power equipment
DE4308004C2 (en) Hydraulic control device for multiple consumers
EP0190431A2 (en) Hydraulic system
DE4416723A1 (en) Hydraulic system with working cylinder, two hydrostatic machines and load
DE3422164C2 (en) Hydraulic system with at least two consumers of hydraulic energy
DE10225691A1 (en) Control device for proportionally adjustable hydraulic pump of closed hydraulic circuit includes valve configuration with valve for each swivel direction of piston and a mechanical touch
DE1176443B (en) Arrangement for the automatic control of liquid gears according to the displacement principle
DE3738241A1 (en) Electrohydraulic device for the load-independent control of a volume flow in a manner proportional to an input signal
DE3820876C2 (en) Hydrostatic steering device
EP0729083A1 (en) Double acting electropneumatic position controller
DE3605649A1 (en) Control device with a pump driven by an adjustable speed engine
EP0211980B1 (en) Driving torque controlling system

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19890816

17Q First examination report despatched

Effective date: 19900711

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

RAP4 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: ROBERT BOSCH GMBH

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3683805

Country of ref document: DE

Date of ref document: 19920319

ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
EAL Se: european patent in force in sweden

Ref document number: 86106864.1

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19960723

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19970506

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19970523

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19970526

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980521

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980531

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19980521

EUG Se: european patent has lapsed

Ref document number: 86106864.1

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050521