EP0832360A1 - Variable displacement electro-hydraulic pump - Google Patents

Variable displacement electro-hydraulic pump

Info

Publication number
EP0832360A1
EP0832360A1 EP95913049A EP95913049A EP0832360A1 EP 0832360 A1 EP0832360 A1 EP 0832360A1 EP 95913049 A EP95913049 A EP 95913049A EP 95913049 A EP95913049 A EP 95913049A EP 0832360 A1 EP0832360 A1 EP 0832360A1
Authority
EP
European Patent Office
Prior art keywords
pump
signal
control
actual value
control valve
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
EP95913049A
Other languages
German (de)
French (fr)
Other versions
EP0832360B1 (en
Inventor
Walter Robeller
Berthold Pfuhl
Volkmar Leutner
Dieter Bertsch
Joachim Zumbraegel
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 EP0832360A1 publication Critical patent/EP0832360A1/en
Application granted granted Critical
Publication of EP0832360B1 publication Critical patent/EP0832360B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/08—Cylinder or housing parameters
    • F04B2201/0804—Noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1205—Position of a non-rotating inclined plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/16—Opening or closing of a valve in a circuit

Definitions

  • the invention relates to an electrohydraulically adjustable pump according to the preamble of the main claim.
  • Such pumps in particular axial, radial or
  • Vane pumps are known in many embodiments and are used in a variety of different areas of application of hydraulics.
  • the main advantages of the electro-hydraulic adjustment of these pumps are the quick and precise electrical controllability and the loss ar ⁇ nut of the drives built with them due to the lack of complex valves between the pump and the consumer.
  • the adjusting pistons of the pumps are pressurized with pressure medium via a control valve.
  • the size relevant for pump adjustment or swiveling, the eccentricity of the cam ring for radial piston pumps and vane pumps or the swivel angle of the swash plate for axial piston pumps is measured with a displacement transducer.
  • This actual value signal of the displacement transducer which is proportional to the pump delivery quantity, is fed to an electronic control amplifier and compared there with the pending setpoint.
  • the actual value of the valve adjustment is fed to this control amplifier, which controls the control valve, via a displacement transducer.
  • the control valve or the pump can be controlled via an internal pressure supply or via an external pressure supply.
  • the adjusting element for example cam ring or swash plate
  • the noise development increases with the falling rigidity of the hydraulic clamping of the adjusting element and is caused by the parts of the engine forces acting in the direction of the adjustment.
  • this leads to a more or less strong deflection of the entire engine in time with the pistons or chambers entering or exiting the pressure chamber of the pump.
  • the additional pulse-shaped control signal is advantageously formed via a speed signal, which is obtained by a conventional speed sensor on the pump.
  • This speed sensor detects the passage of the pump pistons or vanes and generates a corresponding signal.
  • This signal is fed in the form of a trigger signal to a signal converter, which is based on a stored characteristic or a stored characteristic field converts the trigger signal into an additional signal, which is fed to the control amplifier to form the additional control signal.
  • a speed signal which is obtained by a conventional speed sensor on the pump.
  • This speed sensor detects the passage of the pump pistons or vanes and generates a corresponding signal.
  • This signal is fed in the form of a trigger signal to a signal converter, which is based on a stored characteristic or a stored characteristic field converts the trigger signal into an additional signal, which is fed to the control amplifier to form the additional control signal.
  • Operating behavior of the pump generate an adjusted control signal.
  • an adaptation can be optimized, for example, to the nominal operation or to a desired operating behavior.
  • the signal converter is additionally supplied with the actual value of the pump adjustment, since this reduces the influence of the pump adjustment on the operating noise. Since the course of the adjusting force of the adjusting pistons strongly depends on the operating conditions such as eccentricity and pump pressure, it is advantageous if, in addition to the actual value of the pump adjustment, the actual value of the pump pressure generated is also fed to the signal converter as an input signal.
  • the additional control signal can be optimized by appropriately incorporating the disturbance variables acting on the hydraulic clamping of the adjusting element and incorporating it in a characteristic diagram.
  • FIG. 1 shows in Figure 1 the known principle circuit diagram of an electrohydraulically adjustable control pump in an open circuit with a control of the pump or the control valve by means of its own pressure supply.
  • Figure 2 shows a simplified block diagram of the control device according to the invention.
  • the adjustable pump 10 is connected to a pressure medium container 12 via a suction line 11 and conveys this pressure medium via a pressure line 13 to a consumer (not shown).
  • the adjusting element of the pump for example the lifting ring 14 (see FIG. 2), is acted upon or fixed by two oppositely acting adjusting pistons 15 and 16.
  • the adjusting piston 16 with a smaller piston diameter is connected to the pressure line 13 via a control line 17, so that the smaller adjusting piston 16 is constantly acted upon by the delivery pressure.
  • the adjusting piston 15 with a larger effective piston diameter is connected to the control valve 20 via a second control line 18. This is designed, for example, as a 4/4 proportional valve and is moved into its respective switching position by an actuating magnet 21 against the action of a spring 22.
  • the control valve 20 is also connected via a line 23 to the pressure line 13 and via a line 24 to a return line 25 or the pressure medium container 12.
  • the further structure and the mode of operation of the proportional or control valve 20 are not discussed in detail here, since this is known per se and is not essential to the invention.
  • control valve 20 The working position of the control valve 20 is tapped via a displacement transducer 27 and as an actual value signal 36 Control amplifier 28 supplied.
  • this control amplifier 28 is supplied with the working position of the adjusting member 14 as a further actual value 34 via a displacement sensor 29 arranged on the piston pump 10.
  • This control amplifier 28 controls the control valve 20, taking into account the respective input signals.
  • Control line 31 driven by control amplifier 28.
  • An operating setpoint is specified for this control amplifier by a setpoint input 32.
  • the actual value signal 34 of the displacement transducer 29 arranged on the adjusting element 29 is fed to the setpoint specification.
  • the corresponding input signal of the control amplifier 28 is supplied with the actual value signal 36 of the pilot valve from the displacement sensor 27.
  • a speed sensor 38 is arranged on the pump, which generates a signal when a pump piston or vane (not shown) passes by.
  • a trigger signal Up is generated by the speed sensor during operation of the piston pump and is fed to a signal converter 39.
  • This trigger signal Ui is converted on the basis of a characteristic field or a characteristic stored in the signal converter 39 into an additional signal U A , which is fed as a further input signal to the output stage of the control amplifier 28.
  • Additional signal U ⁇ is modified from the trigger signal O ⁇ on the basis of the characteristic curve or the characteristic map stored in the signal converter, so that a superimposed control signal is triggered in the control amplifier 28. This means that the engine forces act on the Compensating force jumps compensated.
  • the additional signal U ⁇ is generated in its course and its phase position so that despite the delays occurring in the control valve 20, a temporal encounter of force jump from the engine and counteraction to the
  • the characteristic curve or the characteristic diagram stored in the signal converter 39 are, for example, based on the nominal operation of the pump, ie the trigger signal U ⁇ is matched in the signal converter 39 on the basis of the stored characteristic curve of the normal operating behavior to the oscillations occurring due to engine power.
  • the signal converter 39 can be supplied with the actual value signal 34 'of the displacement sensor 29 on the adjusting element.
  • the actual value of the pump pressure Pp and / or a signal detected by a sensor 40 on the pump 10 can be given to the converter 39 either individually or in combination with the others
  • a servo valve can also be used for the control valve controlling the adjustment piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

A variable displacement electro-hydraulic pump is operated in a closed loop position control circuit. The adjusting pistons at the adjusting member of the pump are controlled for that purpose by a control valve (20) that in turn is driven by a control amplifier (28). The adjustment path of the control valve and the adjustment path of the adjusting member of the pump are supplied as real values to this control amplifier (28). In addition, an adjusting signal that depends on the angle of rotation of the pump is generated at the control amplifier. This additional pulse-shaped adjusting signal allows the oscillating effects of the driving unit forces on the hydraulic fixation, as well as the resulting noises to be compensated.

Description

Elektrohydraulisch verstellbare PumpeElectrohydraulically adjustable pump
Stand der TechnikState of the art
Die Erfindung geht aus von einer elektrohydraulisch verstellbaren Pumpe nach der Gattung des Hauptanspruchs. Derartige Pumpen, insbesondere Axial-, Radialkolben- oderThe invention relates to an electrohydraulically adjustable pump according to the preamble of the main claim. Such pumps, in particular axial, radial or
Flügelzellenpumpen, sind in vielen Ausfuhrungsformen bekannt und werden in einer Vielzahl von unterschiedlichen Anwendungsbereichen der Hydraulik eingesetzt. Dabei sind die Hauptvorteile der elektrohydraulischen Verstellung dieser Pumpen die schnelle und präzise elektrische Ansteuerbarkeit und die Verlustarτnut der mit ihnen aufgebauten Antriebe wegen des Fehlens von aufwendigen Ventilen zwischen Pumpe und Verbraucher. Die Verstellkolben der Pumpen werden dabei über ein Regelventil mit Druckmittel beaufschlagt. Die für die Pumpenverstellung bzw. -ausSchwenkung maßgebliche Größe, die Exzentrizität des Hubringes bei Radialkolbenpumpen und Flügelzellenpumpen bzw. der Schwenkwinkel der Schrägscheibe bei Axialkolbenpumpen, wird mit einem Wegaufnehmer abgegriffen. Dieses der Pumpenfördermenge proportionale Istwertsignal des Wegaufnehmers wird einem elektronischen Regelverstärker zugeführt und dort mit dem anstehenden Sollwert verglichen. Diesem Regelverstärker, der das Regelventil ansteuert, wird gleichzeitig der Istwert der Ventilverstellung über einen Wegaufnehmer zugeführt. Die Ansteuerung des Regelventils bzw. der Pumpe kann dabei über eine Eigendruck- oder über eine Fremddruckversorgung erfolgen.Vane pumps are known in many embodiments and are used in a variety of different areas of application of hydraulics. The main advantages of the electro-hydraulic adjustment of these pumps are the quick and precise electrical controllability and the loss arτnut of the drives built with them due to the lack of complex valves between the pump and the consumer. The adjusting pistons of the pumps are pressurized with pressure medium via a control valve. The size relevant for pump adjustment or swiveling, the eccentricity of the cam ring for radial piston pumps and vane pumps or the swivel angle of the swash plate for axial piston pumps is measured with a displacement transducer. This actual value signal of the displacement transducer, which is proportional to the pump delivery quantity, is fed to an electronic control amplifier and compared there with the pending setpoint. The actual value of the valve adjustment is fed to this control amplifier, which controls the control valve, via a displacement transducer. The control valve or the pump can be controlled via an internal pressure supply or via an external pressure supply.
Bei derartigen elektrohydraulisch verstellbaren Pumpen wird das Verstellorgan (z.B. Hubring oder Schrägscheibe) von der hydraulischen Einspannung des Verstellorganes abhängig. Die Geräuschentwicklung nimmt mit fallender Steifigkeit der hydraulischen Einspannung des Verstellorganes zu und wird durch die in Richtung der Verstellung wirkenden Anteile der Triebwerkskräfte verursacht. Je nach Steifigkeit der Einspannung führt dies zu einer mehr oder weniger starken Auslenkung des gesamten Triebwerkes im Takt der in den Druckraum der Pumpe ein- bzw. austretenden Kolben bzw. Kammern.In the case of such electrohydraulically adjustable pumps, the adjusting element (for example cam ring or swash plate) is made by dependent on the hydraulic clamping of the adjusting element. The noise development increases with the falling rigidity of the hydraulic clamping of the adjusting element and is caused by the parts of the engine forces acting in the direction of the adjustment. Depending on the rigidity of the clamping, this leads to a more or less strong deflection of the entire engine in time with the pistons or chambers entering or exiting the pressure chamber of the pump.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße elektrohydraulisch verstellbare Pumpe mit den kennzeichnenden Merkmalen des Hauptanspruches hat demgegenüber den Vorteil, daß die Geräuschentwicklung derThe electrohydraulically adjustable pump according to the invention with the characterizing features of the main claim has the advantage that the noise level of the
Pumpe wesentlich verringert wird, indem der Einfluß der auf die hydraulische Einspannung des Verstellorgans einwirkenden Anteile der Triebwerkskräfte vermindert wird, indem diesen entgegengewirkt wird. Durch die erfindungsgemäße Ansteuerung des Regelventils mit einem impulsförmigen zusätzlichen Stellsignal, das vom Drehwinkel der Pumpe abhängig ist, werden die triebwerkskraftbedingten Oszillationen und damit das Betriebsgeräusch günstig beeinflußt. Diese Beeinflussung bzw. Verminderung geht weit über ein Maß hinaus, das mit der konstruktiven Gestaltung des Verstellorganes bzw. derPump is significantly reduced by reducing the influence of the portions of the engine forces acting on the hydraulic clamping of the adjusting member, by counteracting this. Through the control of the control valve according to the invention with a pulse-shaped additional control signal, which is dependent on the angle of rotation of the pump, the engine-force-induced oscillations and thus the operating noise are favorably influenced. This influencing or reduction goes far beyond a measure that is associated with the constructive design of the adjusting member or
Verstellkolben und der regelungstechnischen Auslegung des Lageregelkreises möglich wären.Adjusting piston and the control design of the position control loop would be possible.
Das zusätzliche impulsförmige Stellsignal wird auf vorteilhafte Weise über ein Drehzahlsignal gebildet, das durch einen herkömmlichen Drehzahlsensor an der Pumpe gewonnen wird. Dieser Drehzahlsensor detektiert den Vorbeilauf der Pumpenkolben bzw. -flügel und erzeugt ein entsprechendes Signal. Dieses Signal wird in Form eines Triggersignals einem Signalumformer zugeführt, der anhand einer abgelegten Kennlinie oder eines abgelegten Kennlinienfeldes das Triggersignal in ein Zusatzsignal überführt, welches dem Regelverstärker zur Bildung des zusätzlichen Stellsignals zugeführt wird. Damit läßt sich auf vorteilhafte Weise ein an ein bestimmtesThe additional pulse-shaped control signal is advantageously formed via a speed signal, which is obtained by a conventional speed sensor on the pump. This speed sensor detects the passage of the pump pistons or vanes and generates a corresponding signal. This signal is fed in the form of a trigger signal to a signal converter, which is based on a stored characteristic or a stored characteristic field converts the trigger signal into an additional signal, which is fed to the control amplifier to form the additional control signal. This can be an advantageous to a certain
Betriebsverhalten der Pumpe angepaßtes Stellsignal erzeugen. Durch entsprechende Auswahl der Kennlinie bzw. des Kennlinienfeldes kann eine Anpassung beispielsweise auf den Nennbetrieb bzw. auf ein gewünschtes Betriebsverhalten optimiert werden.Operating behavior of the pump generate an adjusted control signal. By appropriate selection of the characteristic curve or the characteristic field, an adaptation can be optimized, for example, to the nominal operation or to a desired operating behavior.
Besonders vorteilhaft ist es, wenn dem Signalumformer zusätzlich der Istwert der Pumpenverstellung zugeführt wird, da damit der Einfluß der Pumpenverstellung auf das Betriebsgeräusch vermindert wird. Da der Verlauf der Verstellkraft der Verstellkolben stark von den Betriebsbedingungen wie Exzentrizität und Pumpendruck abhängt, ist es vorteilhaft, wenn neben dem Istwert der Pumpenverstellung dem Signalumformer auch der Istwert des erzeugten Pumpendruckes als Eingangssignal zugeführt wird. Durch entsprechende Einbeziehung der auf die hydraulische Einspannung des Verstellorgans einwirkenden Störgrößen und Einbindung in ein Kennfeld kann das zusätzliche Stellsignal optimiert werden.It is particularly advantageous if the signal converter is additionally supplied with the actual value of the pump adjustment, since this reduces the influence of the pump adjustment on the operating noise. Since the course of the adjusting force of the adjusting pistons strongly depends on the operating conditions such as eccentricity and pump pressure, it is advantageous if, in addition to the actual value of the pump adjustment, the actual value of the pump pressure generated is also fed to the signal converter as an input signal. The additional control signal can be optimized by appropriately incorporating the disturbance variables acting on the hydraulic clamping of the adjusting element and incorporating it in a characteristic diagram.
Steht zusätzlich zu den vorgenannten Einflußgrößen auf die hydraulische Einspannung des Verstellorgans ein vom Körperschall der Pumpe abhängiges Meßsignal zur Verfügung, kann über entsprechende Einbindung am Signalumformer ein nochmals verbessertes Optimierungs- bzw. Anpaßverhalten ermöglicht werden.If, in addition to the above-mentioned influencing variables on the hydraulic clamping of the adjusting member, a measurement signal dependent on the structure-borne noise of the pump is available, a further improvement in the optimization or adaptation behavior can be made possible by appropriate integration on the signal converter.
Zeichnung Die Erfindung wird anhand der Beschreibung und der nachfolgenden Zeichnung näher erläutert. Letztere zeigt in Figur 1 das an sich bekannte Prinzip-Schaltbild einer elektrohydraulisch verstellbaren Regelpumpe im offenen Kreis mit einer Ansteuerung der Pumpe bzw. des Regelventils durch Eigendruckversorgung. Figur 2 zeigt ein vereinfachtes Blockschaltbild der erfindungsgemäßen Regeleinrichtung.drawing The invention is explained in more detail on the basis of the description and the drawing below. The latter shows in Figure 1 the known principle circuit diagram of an electrohydraulically adjustable control pump in an open circuit with a control of the pump or the control valve by means of its own pressure supply. Figure 2 shows a simplified block diagram of the control device according to the invention.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Die verstellbare Pumpe 10 ist über eine Saugleitung 11 mit einem Druckmittelbehälter 12 verbunden und fördert dieses Druckmittel über eine Druckleitung 13 zu einem nicht dargestellten Verbraucher. Das Verstellorgan der Pumpe, beispielsweise der Hubring 14 (siehe Figur 2) wird von zwei entgegengesetzt wirkenden Verstellkolben 15 und 16 beaufschlagt bzw. fixiert. Der Verstellkolben 16 mit kleinerem Kolbendurchmesser ist über eine Steuerleitung 17 mit der Druckleitung 13 verbunden, so daß der kleinere Verstellkolben 16 ständig mit dem Fδrderdruck beaufschlagt wird. Der Verstellkolben 15 mit größerem wirksamen Kolbendurchmesser ist über eine zweite Steuerleitung 18 mit dem Regelventil 20 verbunden. Dieses ist beispielsweise als 4/4-Proportionalventil ausgebildet und wird durch einen Stellmagneten 21 gegen die Wirkung einer Feder 22 in seine jeweilige Schaltstellung bewegt. Das Regelventil 20 ist weiterhin über eine Leitung 23 mit der Druckleitung 13 und über eine Leitung 24 mit einer Rücklaufleitung 25 bzw. dem Druckmittelbehälter 12 verbunden. Auf den weiteren Aufbau und die Wirkungweise des Proportional- bzw. Regelventils 20 wird hier nicht näher eingegangen, da dieser an sich bekannt und nicht erfindungswesentlich ist.The adjustable pump 10 is connected to a pressure medium container 12 via a suction line 11 and conveys this pressure medium via a pressure line 13 to a consumer (not shown). The adjusting element of the pump, for example the lifting ring 14 (see FIG. 2), is acted upon or fixed by two oppositely acting adjusting pistons 15 and 16. The adjusting piston 16 with a smaller piston diameter is connected to the pressure line 13 via a control line 17, so that the smaller adjusting piston 16 is constantly acted upon by the delivery pressure. The adjusting piston 15 with a larger effective piston diameter is connected to the control valve 20 via a second control line 18. This is designed, for example, as a 4/4 proportional valve and is moved into its respective switching position by an actuating magnet 21 against the action of a spring 22. The control valve 20 is also connected via a line 23 to the pressure line 13 and via a line 24 to a return line 25 or the pressure medium container 12. The further structure and the mode of operation of the proportional or control valve 20 are not discussed in detail here, since this is known per se and is not essential to the invention.
Die Arbeitsstellung des Regelventils 20 wird über einen Wegaufnehmer 27 abgegriffen und als Istwertsignal 36 einem Regelverstärker 28 zugeführt. Diesem Regelverstärker 28 wird darüberhinaus die Arbeitsstellung des Verstellorganes 14 über einen an der Kolbenpumpe 10 angeordneten Wegaufnehmer 29 als weiterer Istwert 34 zugeführt. Durch diesen Regelverstärker 28 wird unter Einbeziehung der jeweiligen Eingangssignale das Regelventil 20 angesteuert.The working position of the control valve 20 is tapped via a displacement transducer 27 and as an actual value signal 36 Control amplifier 28 supplied. In addition, this control amplifier 28 is supplied with the working position of the adjusting member 14 as a further actual value 34 via a displacement sensor 29 arranged on the piston pump 10. This control amplifier 28 controls the control valve 20, taking into account the respective input signals.
Bei dem in Figur 2 dargestellten Blockschaltbild sind die Pumpe 10 und das Regelventil 20 schematisch dargestellt. Der Stellmagnet 21 des Regelventils 20 wird über eineIn the block diagram shown in Figure 2, the pump 10 and the control valve 20 are shown schematically. The control magnet 21 of the control valve 20 is via a
Steuerleitung 31 vom Regelverstärker 28 angesteuert. Diesem Regelverstärker wird durch eine Sollwerteingabe 32 ein Betriebssollwert vorgegeben. An einem ersten Summierpunkt 33 wird der Sollwertvorgabe das Istwertsignal 34 des am Verstellorgan angeordneten Wegaufnehmers 29 zugeführt. An einem zweiten, nachgeschalteten Summierpunkt 35 wird dem entsprechenden Eingangssignal des Regelverstärkers 28 das Istwertsignal 36 des Vorsteuerventils vom Wegaufnehmer 27 zugeführt.Control line 31 driven by control amplifier 28. An operating setpoint is specified for this control amplifier by a setpoint input 32. At a first summing point 33 the actual value signal 34 of the displacement transducer 29 arranged on the adjusting element 29 is fed to the setpoint specification. At a second, downstream summing point 35, the corresponding input signal of the control amplifier 28 is supplied with the actual value signal 36 of the pilot valve from the displacement sensor 27.
Zusätzlich zu der bisher beschriebenen Signalaufnähme ist an der Pumpe ein Drehzahlsensor 38 angeordnet, der beim Vorbeilauf eines nicht dargestellten Pumpenkolbens oder - Flügels ein Signal erzeugt. Dadurch wird vom Drehzahlsensor beim Betrieb der Kolbenpumpe ein Triggersignal U-p erzeugt, das einem Signalumformer 39 zugeführt wird. Dieses Triggersignal Ui wird anhand eines im Signalumformer 39 abgelegten Kennlinienfeldes bzw. einer Kennlinie in ein Zusatzsignal UA umgewandelt, das als weiteres Eingangssignal der Endstufe des Regelverstärkers 28 zugeführt wird. DasIn addition to the signal recording described so far, a speed sensor 38 is arranged on the pump, which generates a signal when a pump piston or vane (not shown) passes by. As a result, a trigger signal Up is generated by the speed sensor during operation of the piston pump and is fed to a signal converter 39. This trigger signal Ui is converted on the basis of a characteristic field or a characteristic stored in the signal converter 39 into an additional signal U A , which is fed as a further input signal to the output stage of the control amplifier 28. The
Zusatzsignal U^ wird anhand der im Signalumformer abgelegten Kennlinie bzw. des Kennfeldes so aus dem Triggersignal O^ abgewandelt, daß damit im Regelverstärker 28 ein überlagerndes Stellsignal ausgelöst wird. Damit werden die durch die Einwirkung der Triebwerkskräfte auf die Stellkolben wirkenden Kraftsprünge ausgeglichen. Das Zusatzsignal U^ ist dazu in seinem Verlauf und seiner Phasenlage so erzeugt, daß trotz der im Regelventil 20 auftretenden Verzögerungen ein zeitliches Aufeinandertreffen von Kraftsprung aus dem Triebwerk und Gegenaktion an denAdditional signal U ^ is modified from the trigger signal O ^ on the basis of the characteristic curve or the characteristic map stored in the signal converter, so that a superimposed control signal is triggered in the control amplifier 28. This means that the engine forces act on the Compensating force jumps compensated. The additional signal U ^ is generated in its course and its phase position so that despite the delays occurring in the control valve 20, a temporal encounter of force jump from the engine and counteraction to the
Verstellkolben sichergestellt ist. Die im Signalumformer 39 abgelegte Kennlinie bzw. das Kennfeld sind beispielsweise auf den Nennbetrieb der Pumpe abgestellt, d.h. das Triggersignal Uτ wird im Signalumformer 39 anhand der abgelegten Kennlinie des Normalbetriebsverhaltens auf die dabei auftretenden triebwerkskraftbedingten Oszillationen abgestimmt.Adjusting piston is ensured. The characteristic curve or the characteristic diagram stored in the signal converter 39 are, for example, based on the nominal operation of the pump, ie the trigger signal U τ is matched in the signal converter 39 on the basis of the stored characteristic curve of the normal operating behavior to the oscillations occurring due to engine power.
Diese triebwerkskraftbedingten Oszillationen, bzw. der Einfluß der Triebwerkskräfte auf die Verstellkolben bzw. die hydraulische Einspannung sind stark von den Betriebsbedingungen wie Exzentrizität bzw. Verstellung des Verstellorganes und vom erzeugten Pumpendruck abhängig. Daher kann dem Signalumformer 39 zusätzlich zum Triggersignal U-p des Drehzahlsensors 38 das Istwert-Signal 34' des Wegaufnehmers 29 am Verstellorgan zugeführt werden. Als weitere Eingangssignale für den Signalumformer 39 können diesem jeweils für sich oder in Kombination mit den anderen der Istwert des Pumpendruckes Pp und/oder ein durch einen Meßaufnehmer 40 an der Pumpe 10 erfaßtes Signal inThese oscillations caused by the engine power or the influence of the engine forces on the adjusting pistons or the hydraulic clamping are strongly dependent on the operating conditions such as eccentricity or adjustment of the adjusting member and on the pump pressure generated. Therefore, in addition to the trigger signal U-p of the speed sensor 38, the signal converter 39 can be supplied with the actual value signal 34 'of the displacement sensor 29 on the adjusting element. As further input signals for the signal converter 39, the actual value of the pump pressure Pp and / or a signal detected by a sensor 40 on the pump 10 can be given to the converter 39 either individually or in combination with the others
Abhängigkeit vom Körperschall der Pumpe zugeführt werden.Dependent on the structure-borne noise of the pump.
Selbstverständlich sind Änderungen an der gezeigten Ausfuhrungsform möglich, ohne vom Gedanken der Erfindung abzuweichen. So kann für das den Verstellkolben steuernde Regelventil auch ein Servoventil verwendet werden. Of course, changes to the embodiment shown are possible without departing from the spirit of the invention. For example, a servo valve can also be used for the control valve controlling the adjustment piston.

Claims

Ansprüche Expectations
1. Elektrohydraulisch verstellbare Pumpe (10), deren Verstellorgan (14) von mindestens einem Verstellkolben (15, 16) verstellbar ist, der über ein Regelventil (20) beaufschlagt wird, das wiederum von einem Regelverstärker (28) angesteuert wird, dem der Istwert (34) der Pumpenverstellung und der Istwert (36) der Regelventilverstellung zugeführt werden, dadurch gekennzeichnet, daß das Regelventil (20) über den Regelverstärker (28) mit einem zusätzlichen impulsförmigen Stellsignal angesteuert wird, welches vom Drehwinkel der Pumpe (10) abhängig ist.1. Electrohydraulically adjustable pump (10), the adjusting member (14) of which is adjustable by at least one adjusting piston (15, 16), which is acted upon by a control valve (20), which in turn is controlled by a control amplifier (28) to which the actual value (34) the pump adjustment and the actual value (36) of the control valve adjustment, characterized in that the control valve (20) is controlled via the control amplifier (28) with an additional pulse-shaped control signal which is dependent on the angle of rotation of the pump (10).
2. Elektrohydraulisch verstellbare Pumpe nach Anspruch 1, dadurch gekennzeichnet, daß zur Erzeugung des zusätzlichen Stellsignals mindestens ein Drehzahlsensor (38) an der Pumpe (10) angeordnet ist.2. Electrohydraulically adjustable pump according to claim 1, characterized in that at least one speed sensor (38) is arranged on the pump (10) to generate the additional control signal.
3. Elektrohydraulisch verstellbare Pumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß vom Drehzahlsensor (38) mindestens ein Triggersignal U^ erzeugt wird, das einem Signalumformer (39) zugeführt wird,der anhand einer abgelegten Kennlinie oder eines abgelegten Kennlinienfeldes das Triggersignal U^ in ein modifiziertes Zusatzsignal U^ überführt, welches am Regelverstärker (28) zur Bildung des zusätzlichen Stellsignals zugeführt wird.3. Electrohydraulically adjustable pump according to claim 1 or 2, characterized in that at least one trigger signal U ^ is generated by the speed sensor (38), which is fed to a signal converter (39) which uses a stored characteristic or a stored characteristic field to generate the trigger signal U ^ converted into a modified additional signal U ^, which is fed to the control amplifier (28) to form the additional control signal.
4. Elektrohydraulisch verstellbare Pumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß dem Signalumformer zusätzlich der Istwert (34') der Pumpenverstellung zugeführt wird. 4. Electrohydraulically adjustable pump according to one of claims 1 to 3, characterized in that the signal converter additionally the actual value (34 ') of the pump adjustment is supplied.
5. Elektrohydraulisch vestellbare Pumpe nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß dem Signalumformer (39) zusätzlich der Istwert des erzeugten Pumpendruckes Pp zugeführt wird.5. Electro-hydraulically adjustable pump according to one of claims 1 to 3, characterized in that the signal converter (39) is additionally supplied with the actual value of the pump pressure Pp generated.
6. Elektrohydraulisch verstellbare Pumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß dem Signalumformer (39) zusätzlich ein vom erzeugten Körperschall der Pumpe (10) abhängiges Schallsignal zugeführt wird.6. Electrohydraulically adjustable pump according to one of claims 1 to 5, characterized in that the signal converter (39) is additionally supplied with a sound signal which is dependent on the structure-borne sound of the pump (10).
7. Elektrohydraulisch verstellbare Pumpe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß das Zusatzsignal UA unter Umgehung der Regler im Regelverstärker (28) direkt dessen Endstufe zugeführt wird.7. Electro-hydraulically adjustable pump according to one of claims 1 to 6, characterized in that the additional signal U A , bypassing the controller in the control amplifier (28) is supplied directly to its output stage.
8. Elektrohydraulisch verstellbare Pumpe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Pumpe als axial oder radial arbeitende Kolbenpumpe (10) oder als Flügelzellenpumpe ausgebildet ist. 8. Electrohydraulically adjustable pump according to one of claims 1 to 7, characterized in that the pump is designed as an axially or radially operating piston pump (10) or as a vane pump.
EP95913049A 1994-03-28 1995-03-23 Variable displacement electro-hydraulic pump Expired - Lifetime EP0832360B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4410719 1994-03-28
DE4410719A DE4410719A1 (en) 1994-03-28 1994-03-28 Electrohydraulically adjustable pump
PCT/DE1995/000402 WO1995026470A1 (en) 1994-03-28 1995-03-23 Variable displacement electro-hydraulic pump

Publications (2)

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EP0832360A1 true EP0832360A1 (en) 1998-04-01
EP0832360B1 EP0832360B1 (en) 1999-09-08

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US (1) US5879136A (en)
EP (1) EP0832360B1 (en)
JP (1) JPH09510764A (en)
KR (1) KR100329451B1 (en)
DE (2) DE4410719A1 (en)
WO (1) WO1995026470A1 (en)

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DE102008061828A1 (en) 2008-12-11 2010-06-17 Robert Bosch Gmbh Hydrostatic pump i.e. axial piston pump, has drive shaft rotatably supported in housing, so that rotary motion of drive shaft is superimposed with oscillation movement in terms of avoidance of pulsation by actuator
US8429908B2 (en) 2009-12-17 2013-04-30 Deere & Company Hydraulic system

Also Published As

Publication number Publication date
JPH09510764A (en) 1997-10-28
WO1995026470A1 (en) 1995-10-05
DE4410719A1 (en) 1995-10-05
KR100329451B1 (en) 2002-09-05
KR970701832A (en) 1997-04-12
DE59506814D1 (en) 1999-10-14
EP0832360B1 (en) 1999-09-08
US5879136A (en) 1999-03-09

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