EP1930604B1 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
EP1930604B1
EP1930604B1 EP20070022458 EP07022458A EP1930604B1 EP 1930604 B1 EP1930604 B1 EP 1930604B1 EP 20070022458 EP20070022458 EP 20070022458 EP 07022458 A EP07022458 A EP 07022458A EP 1930604 B1 EP1930604 B1 EP 1930604B1
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EP
European Patent Office
Prior art keywords
pressure
brake valve
control
hydraulic
control device
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.)
Not-in-force
Application number
EP20070022458
Other languages
German (de)
French (fr)
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EP1930604A3 (en
EP1930604A2 (en
Inventor
Gerold Liebler
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1930604A2 publication Critical patent/EP1930604A2/en
Publication of EP1930604A3 publication Critical patent/EP1930604A3/en
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Publication of EP1930604B1 publication Critical patent/EP1930604B1/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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hydraulic control arrangement according to the preamble of patent claim 1.
  • Hydraulic control arrangements in which the hydraulic consumer is driven directly by an adjustable pressure medium source, ie a variable displacement pump and is controlled by the control or regulation of the variable displacement pump in terms of its speed or force, are very efficient.
  • an adjustable pressure medium source ie a variable displacement pump and is controlled by the control or regulation of the variable displacement pump in terms of its speed or force.
  • a typical application is a plastic injection machine in which 5 to 6 hydraulic axes are moved one after the other and always individually within the injection cycle.
  • An adjustable, pressure-controlled or volume flow-controlled pressure medium source that can be used for such an application is described in the applicant's data sheet RD 30630 / 06.06.
  • the simplest construction of such a hydraulic control arrangement is that of an open hydraulic circuit.
  • the pressure medium is supplied by the consumer to the pressure medium tank.
  • a brake valve is usually arranged in the pressure medium line from the consumer to the pressure medium tank.
  • the brake valve throttles the outflow of pressure medium to the pressure medium tank to brake the consumer.
  • the brake valve is actuated by the pressure with which the load is supplied to the source side.
  • Such a brake valve is shown in RE 64 298 / 09.97.
  • the essential component of the brake valve is a hydraulically actuated 2/2-way proportional valve. When pressure is removed from the control input, a spring controls the 2/2-way proportional valve, which throttles the connection between the consumer and the tank and slows down the consumer due to the accumulated pressure medium.
  • the brake valve causes a hydrostatic feedback to its input signal, namely the pressure of the pressure medium supplied to the consumer.
  • the damping of the brake valve and its accumulation line must each be tailored to the hydraulic control arrangement. This has a high technical and personnel costs for the establishment of such control orders result.
  • the voting process requires a detailed knowledge of the respective control arrangement and is therefore to be accomplished only by appropriately trained persons.
  • EP 1 403 529 A2 deals with a method of distributing fluid between multiple hydraulic functions.
  • a pump is used to actuate hydraulic actuators.
  • Via a return line the fluid is returned to a tank.
  • a control valve is arranged in the return line.
  • a controller controls the control valve using pressure signals.
  • the drive system has a pressure medium tank, a pressure medium from the tank sucking and discharging into a supply line hydraulic pump with variable delivery, a double-acting hydraulic consumer, in particular a hydraulic cylinder from which the load is movable, and a directional control valve with a Inlet connection, with an outlet connection connected to the pressure medium tank, with two load connections and with a centered by at least one centering spring in a neutral position and displaceable from the neutral position control piston.
  • a pressure medium tank a pressure medium from the tank sucking and discharging into a supply line hydraulic pump with variable delivery
  • a double-acting hydraulic consumer in particular a hydraulic cylinder from which the load is movable
  • a directional control valve with a Inlet connection, with an outlet connection connected to the pressure medium tank, with two load connections and with a centered by at least one centering spring in a neutral position and displaceable from the neutral position control piston.
  • a directional control valve with a Inlet connection, with an outlet connection connected to the pressure
  • EP 1 338 802 A2 deals with a hydraulic control circuit for operating two hydraulic cylinders.
  • the present invention is therefore directed to provide a simpler and in particular with less coordination effort afflicted hydraulic control arrangement of the type described above.
  • a hydraulic control arrangement is equipped with an adjustable pressure medium source for controlling a hydraulic consumer with a pressure medium.
  • an electronic control system for controlling an actuator of the pressure medium source and a brake valve, by which a hydraulic connection between the consumer and a pressure medium tank can be throttled provided.
  • the peculiarity is that the brake valve can be controlled arbitrarily by an electromechanical actuator.
  • This makes it possible to control the brake valve by robust and easily configurable electronic control or regulating mechanisms.
  • the electronic control mechanism may be designed to operate reliably, in a predetermined manner and in particular without oscillations in the braking phase, without adaptation for a plurality of the usual applications.
  • a simple parameter-based configuration can be provided.
  • the aforementioned advantages reduce the installation effort of the hydraulic control device, increase their maintenance and ease of use and also ensure increased acceptance by the customer.
  • the brake valve with electromechanical actuator can be represented by a simple, available in mass production proportional directional control valve. This may possibly be cheaper available than a brake valve of conventional design.
  • the control electronics is connected to the actuating device of the brake valve.
  • the variable, the associated control electronics and the brake valve forms a ready-to-use preconfigurable drive system that can be easily integrated by the user in their own application.
  • the control electronics forms a uniform interface for controlling the consumer by means of variable and brake valve. If the control electronics includes a microcontroller, this conventional way still has sufficient resources to control the brake valve can. Therefore, the hardware complexity in the control of the brake valve by the control electronics of the variable is very low.
  • the control electronics detects a pressure actual value and / or volume flow actual value of the pressure medium source and, based on this, forms an actuation signal for the brake valve.
  • the said signals are available for the regulation of the variable displacement of the pressure medium source anyway. They can be used without additional recording effort to control the brake valve. It is also advantageous to form the actuation signal on the basis of a time derivative of the actual pressure value or of the actual volume flow value. By using the derivative signal, among other things, an oscillation tendency of the drive during braking can be reduced.
  • control electronics form the actuation signal for the brake valve on the basis of a pressure set value supplied to it and / or volumetric flow setpoint of the pressure medium source, a feedback can be avoided even better. In addition, it enables precise, fast and, if necessary, even abrupt braking.
  • the control electronics automatically selects a pressure or a volume flow control of the pressure medium source and forms in dependence on the selected control mechanism, the actuation signal for the brake valve.
  • a complete closing of the brake valve e.g. have a disturbing effect, because then it is not sure whether the force generated by the pressure in the pressure medium on the consumer actually acts on a workpiece. This can be prevented by including the operating state, ie the selected control mechanism.
  • a predetermined in the case of pressure control minimum throttling by the brake valve can prevent a runaway or overshoot of the consumer when breaking away an opposing force.
  • a good match between the speed of the load and the volume flow actual value can be achieved by setting a minimum brake pressure.
  • control electronics comprises a pump control component for the control of a variable displacement pump and a Bremsventilan Kunststoffkomponenten for driving the brake valve, both of which are arranged in a common housing. This facilitates the assembly and setup of the hydraulic control assembly.
  • a particularly preferred embodiment provides that the housing is arranged on the variable displacement pump. This allows a compact design of the hydraulic control arrangement and the presentation as a user-friendly, easy to handle and controllable functional unit.
  • control electronics starting from a drive signal for a pilot valve of the pressure medium source forms an actuating signal for the brake valve. Since the control signal for the pilot valve corresponds approximately to a time derivative of the flow rate actual value, it can be used to improve the time response in braking phases.
  • FIG. 1 is the hydraulic control assembly 1 for controlling a hydraulic consumer 2 with a variable displacement pump 5, a 4/2-way switching valve 7 for adjusting the direction of movement of the consumer 2 and equipped with a brake valve 9.
  • the brake valve 9 is arranged in the pressure medium line between the consumer 2 and the pressure medium tank 3 and designed as a continuously adjustable 2/2-way valve. By a proportional solenoid 10, the brake valve 9 is actuated.
  • a swash plate axial piston machine is used as a variable displacement pump 5, a swash plate axial piston machine is used. About the actuating piston 12, the pivot angle of the swash plate and thus the scoop volume of the variable 5 is set. A spring element 13 ensures a deflection of the swash plate in the unpressurized state. The swivel angle detects a swivel angle sensor 14. The swivel angle is a measure of the pumping volume of the pump and also for the flow rate, if one assumes a constant drive speed.
  • the actuating piston 12 is controlled via a pilot valve 16.
  • the pilot valve 16 is designed as a continuous valve and equipped with a proportional solenoid 17 and a separate displacement sensor 18 for detecting the valve position. Downstream of the output terminal of the variable displacement pump 5, a pressure sensor 20 is arranged to detect the output pressure of the variable displacement pump 5.
  • a regulation and control electronics 25 includes a pump regulator component 26 and a brake valve control component 28.
  • the pump regulator component 26 and the brake valve control component 28 are housed in a common housing (not shown).
  • the pump control component 26 is supplied with the actual value signals of the pressure sensor 20, the swivel angle sensor 14, the displacement sensor 18 and a pressure setpoint value applied to an input connection 30 and / or a volumetric flow setpoint value.
  • the pump regulator component 26 regulates the swivel angle of the variable displacement pump 5 on the basis of the actual value signals and setpoint signals supplied to it.
  • the pump regulator component 26 has inter alia a regulator for the output pressure and a regulator for the flow rate.
  • the brake valve control component 28 receives at least one of the following input signals: the actual pressure value, the actual swivel angle value, the desired value for pressure or delivery flow. It is of course also possible to use a plurality of said actual values or desired values in combination as input signals of the brake valve control component 28.
  • the pump controller component 26 can provide a signal 32 which indicates which of the variables-pressure, flow or power-is currently being regulated.
  • the pressure detected at the sensor 20 can be used as a control variable for controlling the control valve 9.
  • the brake valve control component 28 applies e.g. below a certain pressure threshold a to the output pressure of the variable displacement pump 5 inversely proportional actuation current for the proportional magnet 10 is generated.
  • the control characteristic can be influenced electronically and adapted very easily. Thus, unwanted vibrations during braking can be avoided by a suitable damping or by a frequency-selective filter.
  • the actual pressure value can be subjected to a time derivation and the derived pressure actual value can be used as a control signal for the brake valve.
  • the brake valve is actuated only at a pressure drop. This allows a more stable control behavior and energy savings for the pump drive can be achieved.
  • the swivel angle - as a measure of the actual flow - or its time derivative for controlling the brake valve 9 can be used by the brake valve control component 28.
  • the speed of the load 2 is largely proportional to the swing angle during acceleration and constant speed travel.
  • By controlling the brake valve 9 with a control current proportional to the time derivative of the swivel angle signal can be a quick reaction of the consumer to a swivel angle return - ie in the braking phases - achieve. The speed of the consumer thus follows even with a flow reduction, the predetermined flow profile.
  • the control of the brake valve 9 is feedback-free.
  • the reaction rate of the control of the brake valve 9 can be significantly increased.
  • a control delay between the setpoint input 30 and the actual value signals measured at the sensors 14 and 20 does not affect the activation of the brake valve.
  • Very fast and powerful braking is possible. Due to the backpressure built up during the braking process, which acts back on the output of the variable displacement pump 5, a return operation of the variable displacement pump 5 is accelerated.
  • a feedback-free control of the brake valve 9 is ensured even when using the desired pressure signal or its derivative.
  • signal 32 e.g. in a pressure control phase by setting the brake valve 9 in a throttle position a passage of the consumer can be prevented when breaking away a counterforce.
  • the brake valve to minimize the energy consumption can be fully opened.
  • a certain detectable at the pressure sensor 20 minimum backpressure to reduce the influence of disturbances on the movement of the consumer and to ensure a high degree of proportionality between the swivel angle signal and the speed of the consumer 2.
  • variable displacement pump 5 may comprise, instead of a swash plate type axial piston pump, all known variable displacement hydraulic machines accessible to pressure or flow control, e.g. Axialkoibenpumpen in Schrägachsenbauweise, vane pumps or radial piston pumps.
  • the pump regulator component 26 and the brake valve control component 28 can be implemented in analog circuit technology or particularly advantageously as program modules of a control / control program of a microcontroller be educated. Due to the already existing input signals - the signals of the sensors 14 and 20 and the setpoint signals - the additional hardware effort is exhausted in an additional amplifier stage 10 required for driving the proportional magnet 10.
  • the amplifier stage can be mounted on the valve, for example. In the control electronics 25 and then no additional hardware is required compared to a conventional pump control electronics.
  • the brake valve as part of a scheme.
  • the pressure accumulated by the brake valve is detected via its own pressure sensor or via the pressure sensor 20 and used as a controlled variable.
  • this could also be operated without an electrical pressure feedback or swivel angle feedback, and e.g. only have a hydrostatic pressure feedback to the actuator piston 12 or a similar actuator.
  • the brake valve can be controlled arbitrarily by an electromechanical actuator. This makes it possible to control the brake valve by robust and easily configurable electronic control or regulating mechanisms. In addition, a control can be done with little effort by the control electronics of the adjustable pressure medium source.

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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)
  • Braking Systems And Boosters (AREA)
  • Regulating Braking Force (AREA)

Description

Die Erfindung betrifft eine hydraulische Steueranordnung gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic control arrangement according to the preamble of patent claim 1.

Hydraulische Steueranordnungen, bei denen der hydraulische Verbraucher direkt von einer verstellbaren Druckmittelquelle, also einer Verstellpumpe angetrieben wird und durch die Ansteuerung bzw. Regelung der Verstellpumpe hinsichtlich seiner Geschwindigkeit oder der Kraftwirkung gesteuert wird, sind sehr effizient. Durch den Verzicht auf die herkömmlicher Weise im Druckmittelpfad zwischen der Druckmittelquelle und dem Verbraucher verwendeten Proportionalventile zur Geschwindigkeits- oder Drucksteuerung entfallen hydraulische Widerstände im Druckmittelpfad. Der energetische Wirkungsgrad ist sehr hoch. Die Versorgung mehrerer Verbraucher ist allerdings aufwendig, da jeder Verbraucher von einer eigenen Verstellpumpe versorgt werden müsste. Daher wird diese Art der hydraulischen Steuerung vorzugsweise eingesetzt wenn nur wenige oder sogar nur ein (Haupt-) Verbraucher vorhanden ist, oder wenn mehrere Verbraucher vorhanden sind, die nicht gleichzeitig sondern gemäß einem Zeitschema einzeln und nacheinander bewegt werden. Eine typische Anwendung ist eine Kunststoffspritzmaschine, bei der innerhalb des Spritzzyklus 5 bis 6 hydraulische Achsen nacheinander und immer einzeln verfahren werden. Eine verstellbare, druckgeregelte oder volumenstromgeregelte Druckmittelquelle, die für eine solche Anwendung einsetzbar ist, ist im Datenblatt RD 30630/06.06 der Anmelderin beschrieben.Hydraulic control arrangements in which the hydraulic consumer is driven directly by an adjustable pressure medium source, ie a variable displacement pump and is controlled by the control or regulation of the variable displacement pump in terms of its speed or force, are very efficient. By dispensing with the conventional manner used in the pressure medium path between the pressure medium source and the consumer proportional valves for speed or pressure control eliminates hydraulic resistances in the pressure medium path. The energy efficiency is very high. However, the supply of several consumers is complicated, since each consumer would have to be supplied by its own variable displacement pump. Therefore, this type of hydraulic control is preferably used when only a few or even only one (main) consumer is present, or when there are several consumers that are not moved simultaneously but according to a time scheme individually and sequentially. A typical application is a plastic injection machine in which 5 to 6 hydraulic axes are moved one after the other and always individually within the injection cycle. An adjustable, pressure-controlled or volume flow-controlled pressure medium source that can be used for such an application is described in the applicant's data sheet RD 30630 / 06.06.

Der einfachste Aufbau einer solchen hydraulischen Steueranordnung ist der eines offenen hydraulischen Kreises. Dabei wird das Druckmittel vom Verbraucher dem Druckmitteltank zugeführt. Da bei dieser Konfiguration das Abbremsen des Verbrauchers nur unzureichend gelingt, wird meist in der Druckmittelleitung vom Verbraucher zum Druckmitteltank ein Bremsventil angeordnet. Das Bremsventil drosselt den Abfluss von Druckmittel zum Druckmitteltank um den Verbraucher zu bremsen. In herkömmlichen Steueranordnungen wird das Bremsventil durch den Druck, mit dem der Verbraucher quellenseitig beaufschlagt wird, angesteuert. Ein solches Bremsventil zeigt die RD 64 298/09.97. Die wesentliche Komponente des Bremsventils ist ein hydraulisch angesteuertes 2/2-Wege-Stetigventil. Bei Wegfall der Druckbeaufschlagung am Steuereingang steuert eine Feder das 2/2-Wege-Stetigventil zu, wodurch die Verbindung des Verbrauchers zum Tank gedrosselt wird und der Verbraucher durch das aufgestaute Druckmittel abgebremst wird.The simplest construction of such a hydraulic control arrangement is that of an open hydraulic circuit. The pressure medium is supplied by the consumer to the pressure medium tank. Because with this configuration the Deceleration of the consumer succeeds only insufficiently, a brake valve is usually arranged in the pressure medium line from the consumer to the pressure medium tank. The brake valve throttles the outflow of pressure medium to the pressure medium tank to brake the consumer. In conventional control arrangements, the brake valve is actuated by the pressure with which the load is supplied to the source side. Such a brake valve is shown in RE 64 298 / 09.97. The essential component of the brake valve is a hydraulically actuated 2/2-way proportional valve. When pressure is removed from the control input, a spring controls the 2/2-way proportional valve, which throttles the connection between the consumer and the tank and slows down the consumer due to the accumulated pressure medium.

Bei der beschriebenen herkömmlichen hydraulische Steueranordnung verursacht das Bremsventil eine hydrostatische Rückkopplung auf sein Eingangssignal, nämlich den Druck des dem Verbraucher zugeführten Druckmittels. Zur Verhinderung von unerwünschten Oszillationen beim Bremsvorgang muss die Dämpfung des Bremsventils und seine Staukennlinie jeweils individuell auf die hydraulische Steueranordnung abgestimmt werden. Dies hat einen hohen technischen und personellen Aufwand für die Einrichtung solcher Steueranordnungen zu Folge. Zudem setzt der Abstimmungsvorgang eine detaillierte Kenntnis der jeweiligen Steueranordnung voraus und ist daher nur von entsprechend geschulten Personen zu bewerkstelligen.In the described conventional hydraulic control arrangement, the brake valve causes a hydrostatic feedback to its input signal, namely the pressure of the pressure medium supplied to the consumer. To prevent unwanted oscillations during braking, the damping of the brake valve and its accumulation line must each be tailored to the hydraulic control arrangement. This has a high technical and personnel costs for the establishment of such control orders result. In addition, the voting process requires a detailed knowledge of the respective control arrangement and is therefore to be accomplished only by appropriately trained persons.

EP 1 403 529 A2 befasst sich mit einem Verfahren zum Verteilen von Fluid zwischen mehreren hydraulischen Funktionen. Dabei wird eine Pumpe zur Betätigung von hydraulischen Aktuatoren eingesetzt. Über eine Rückführleitung wird das Fluid zu einem Tank zurückgeführt. Ein Steuerventil ist in der Rückführleitung angeordnet. Eine Steuerung steuert das Steuerventil unter Verwendung von Drucksignalen. EP 1 403 529 A2 deals with a method of distributing fluid between multiple hydraulic functions. In this case, a pump is used to actuate hydraulic actuators. Via a return line, the fluid is returned to a tank. A control valve is arranged in the return line. A controller controls the control valve using pressure signals.

DE 199 50 910 A1 befasst sich mit einem Antriebssystem für eine Last. Das Antriebssystem besitzt einen Druckmitteltank, eine Druckmittel aus dem Tank ansaugende und in eine Zulaufleitung abgebende Hydropumpe mit veränderbarer Fördermenge, einen doppeltwirkenden hydraulischen Verbraucher, insbesondere einen Hydrozylinder, von dem die Last bewegbar ist, und ein Wegeventil mit einem Zulaufanschluß, mit einem mit dem Druckmitteltank verbundenenAblaufanschluß, mit zwei Verbraucheranschlüssen und mit einem durch wenigstens eine Zentrierfeder in eine Neutralstellung zentrierten und aus der Neutralstellung verschiebbaren Steuerkolben. In Abhängigkeit von der Rückstellung des Steuerkolbens in Richtung zur Neutralstellung hin ist im Wesentlichen nur der Ablaufdurchflußquerschnitt abdrosselbar. DE 199 50 910 A1 deals with a drive system for a load. The drive system has a pressure medium tank, a pressure medium from the tank sucking and discharging into a supply line hydraulic pump with variable delivery, a double-acting hydraulic consumer, in particular a hydraulic cylinder from which the load is movable, and a directional control valve with a Inlet connection, with an outlet connection connected to the pressure medium tank, with two load connections and with a centered by at least one centering spring in a neutral position and displaceable from the neutral position control piston. Depending on the provision of the control piston in the direction of the neutral position, essentially only the flow-through flow cross-section can be throttled.

EP 1 338 802 A2 befasst sich mit einer hydraulischen Steuerschaltung zum Betreiben zweier hydraulischer Zylinder. EP 1 338 802 A2 deals with a hydraulic control circuit for operating two hydraulic cylinders.

Die vorliegende Erfindung ist daher darauf gerichtet, eine einfachere und insbesondere mit weniger Abstimmungsaufwand behaftete hydraulische Steueranordnung der eingangs beschriebenen Art anzugeben.The present invention is therefore directed to provide a simpler and in particular with less coordination effort afflicted hydraulic control arrangement of the type described above.

Diese Aufgabe wird durch eine hydraulische Steueranordnung mit den Merkmalen des Patentanspruchs 1 gelöst.This object is achieved by a hydraulic control arrangement having the features of patent claim 1.

Erfindungsgemäß ist eine hydraulische Steueranordnung mit einer verstellbaren Druckmittelquelle zur Ansteuerung eines hydraulischen Verbrauchers mit einem Druckmittel ausgestattet. Außerdem sind eine Steuerelektronik zur Ansteuerung eines Stellorgans der Druckmittelquelle und ein Bremsventil, durch welches eine hydraulische Verbindung zwischen dem Verbraucher und einem Druckmitteltank drosselbar ist, vorgesehen.According to the invention a hydraulic control arrangement is equipped with an adjustable pressure medium source for controlling a hydraulic consumer with a pressure medium. In addition, an electronic control system for controlling an actuator of the pressure medium source and a brake valve, by which a hydraulic connection between the consumer and a pressure medium tank can be throttled provided.

Die Besonderheit ist es, dass das Bremsventil durch eine elektromechanische Betätigungsvorrichtung willkürlich ansteuerbar ist. Dies ermöglicht es, das Bremsventil durch robuste und einfach konfigurierbare elektronische Regel-oder Steuermechanismen anzusteuern. Der elektronische Steuermechanismus kann so gestaltet werden, dass er ohne eine Anpassung für eine Vielzahl der üblichen Anwendungsfälle zuverlässig, in vorgegebener Weise und insbesondere ohne Oszillationen in der Bremsphase arbeitet. Zudem kann eine einfache parametergestützte Konfiguration vorgesehen werden. Die vorgenannten Vorteile erniedrigen den Installationsaufwand der hydraulischen Steuervorrichtung, erhöhen ihre Wartungs- und Benutzerfreundlichkeit und sorgen zudem für eine erhöhte Akzeptanz beim Kunden. Das Bremsventils mit elektromechanischer Betätigungsvorrichtung lässt sich durch ein einfaches, in Großserienproduktion verfügbares Proportional-Wegeventil darstellen. Dies kann ggf. kostengünstiger zur Verfügung stehen als ein Bremsventil herkömmlicher Bauart.The peculiarity is that the brake valve can be controlled arbitrarily by an electromechanical actuator. This makes it possible to control the brake valve by robust and easily configurable electronic control or regulating mechanisms. The electronic control mechanism may be designed to operate reliably, in a predetermined manner and in particular without oscillations in the braking phase, without adaptation for a plurality of the usual applications. In addition, a simple parameter-based configuration can be provided. The aforementioned advantages reduce the installation effort of the hydraulic control device, increase their maintenance and ease of use and also ensure increased acceptance by the customer. The brake valve with electromechanical actuator can be represented by a simple, available in mass production proportional directional control valve. This may possibly be cheaper available than a brake valve of conventional design.

Vorteilhafte Ausgestaltungen der vorliegenden Erfindung sind in den Unteransprüchen angegeben.Advantageous embodiments of the present invention are specified in the subclaims.

Gemäß einer besonders bevorzugten Weiterbildung der vorliegenden Erfindung ist die Steuerelektronik mit der Betätigungsvorrichtung des Bremsventils verbunden. Somit bildet die Verstellpumpe, die zugehörige Steuerelektronik und das Bremsventil ein betriebsfertig vorkonfigurierbares Antriebssystem, das vom Benutzer leicht in die eigene Anwendung integriert werden kann. Die Steuerelektronik bildet dabei eine einheitliche Schnittstelle für die Ansteuerung des Verbrauchers mittels Verstellpumpe und Bremsventil. Wenn die Steuerelektronik einen Mikrokontroller umfasst, besitzt dieser üblicher Weise noch ausreichend Ressourcen, um auch das Bremsventil ansteuern zu können. Daher ist der Hardwareaufwand bei der Ansteuerung des Bremsventils durch die Steuerelektronik der Verstellpumpe sehr gering.According to a particularly preferred embodiment of the present invention, the control electronics is connected to the actuating device of the brake valve. Thus, the variable, the associated control electronics and the brake valve forms a ready-to-use preconfigurable drive system that can be easily integrated by the user in their own application. The control electronics forms a uniform interface for controlling the consumer by means of variable and brake valve. If the control electronics includes a microcontroller, this conventional way still has sufficient resources to control the brake valve can. Therefore, the hardware complexity in the control of the brake valve by the control electronics of the variable is very low.

Vorzugsweise erfasst die Steuerelektronik einen Druck-Istwert und/oder Volumenstrom-Istwert der Druckmittelquelle und bildet davon ausgehend ein Betätigungssignal für das Bremsventil. Die genannten Signale liegen für die Regelung der Verstellpumpe der Druckmittelquelle ohnehin vor. Sie können ohne zusätzlichen Erfassungsaufwand zur Steuerung des Bremsventils verwendet werden. Vorteilhaft ist es auch, ausgehend von einer zeitlichen Ableitung des Druck-Istwerts bzw. des Volumenstrom-Istwerts das Betätigungssignal zu bilden. Durch die Verwendung des Ableitungssignals kann unter Anderem eine Oszillationsneigung des Antriebs beim Bremsen vermindert werden.Preferably, the control electronics detects a pressure actual value and / or volume flow actual value of the pressure medium source and, based on this, forms an actuation signal for the brake valve. The said signals are available for the regulation of the variable displacement of the pressure medium source anyway. They can be used without additional recording effort to control the brake valve. It is also advantageous to form the actuation signal on the basis of a time derivative of the actual pressure value or of the actual volume flow value. By using the derivative signal, among other things, an oscillation tendency of the drive during braking can be reduced.

Wenn die die Steuerelektronik ausgehend von einem ihr zugeführten Druck-Sollwert und/oder Volumenstrom-Sollwert der Druckmittelquelle das Betätigungssignal für das Bremsventil bildet, lässt sich eine Rückkopplung noch besser vermeiden. Außerdem werden so präzise, schnelle und bei Bedarf sogar abrupte Bremsvorgänge ermöglicht.If the control electronics form the actuation signal for the brake valve on the basis of a pressure set value supplied to it and / or volumetric flow setpoint of the pressure medium source, a feedback can be avoided even better. In addition, it enables precise, fast and, if necessary, even abrupt braking.

Gemäß der vorliegenden Erfindung wählt die Steuerelektronik automatisch eine Druck- oder eine Volumenstromregelung der Druckmittelquelle und bildet in Abhängigkeit von dem gewählten Regelmechanismus das Betätigungssignal für das Bremsventil. Bei einem druckgeregelten Betrieb kann ein vollständiges Schließen des Bremsventils z.B. störend wirken, da dann nicht sichergestellt ist, ob die durch den Druck im Druckmittel am Verbraucher erzeugte Kraft tatsächlich auf ein Werkstück wirkt. Dies lässt sich durch die Einbeziehung des Betriebszustands, also des gewählten Regelmechanismus, verhindern. Auch kann eine im Fall der Druckregelung vorgegebene Mindestdrosselung durch das Bremsventil ein Durchgehen oder Überschwingen des Verbrauchers bei Wegbrechen einer Gegenkraft verhindern. Im Volumenstromregelbetrieb kann eine gute Übereinstimmung zwischen der Geschwindigkeit des Verbrauchers und dem Volumenstrom-Istwert durch Einstellen eines Mindestbremsdrucks erzielt werden.According to the present invention, the control electronics automatically selects a pressure or a volume flow control of the pressure medium source and forms in dependence on the selected control mechanism, the actuation signal for the brake valve. In a pressure-controlled operation, a complete closing of the brake valve, e.g. have a disturbing effect, because then it is not sure whether the force generated by the pressure in the pressure medium on the consumer actually acts on a workpiece. This can be prevented by including the operating state, ie the selected control mechanism. Also, a predetermined in the case of pressure control minimum throttling by the brake valve can prevent a runaway or overshoot of the consumer when breaking away an opposing force. In the volume flow control mode, a good match between the speed of the load and the volume flow actual value can be achieved by setting a minimum brake pressure.

Gemäß einer bevorzugten Weiterbildung umfasst die Steuerelektronik eine Pumpenreglerkomponente für die Regelung einer Verstellpumpe und eine Bremsventilansteuerkomponenten zur Ansteuerung des Bremsventils, die beide in einem gemeinsamen Gehäuse angeordnet sind. Dies erleichtert die Montage und Einrichtung der hydraulischen Steueranordnung.According to a preferred embodiment, the control electronics comprises a pump control component for the control of a variable displacement pump and a Bremsventilansteuerkomponenten for driving the brake valve, both of which are arranged in a common housing. This facilitates the assembly and setup of the hydraulic control assembly.

Eine besonders bevorzugte Ausgestaltung sieht vor, dass das Gehäuse an der Verstellpumpe angeordnet ist. Dies ermöglicht eine kompakte Bauform der hydraulischen Steueranordnung und die Darstellung als benutzerfreundliche, einfach handhabbare und ansteuerbare Funktionseinheit.A particularly preferred embodiment provides that the housing is arranged on the variable displacement pump. This allows a compact design of the hydraulic control arrangement and the presentation as a user-friendly, easy to handle and controllable functional unit.

Gemäß der Erfindung bildet die Steuerelektronik ausgehend von einem Ansteuersignal für ein Vorsteuerventil der Druckmittelquelle ein Betätigungssignal für das Bremsventil. Da das Ansteuersignal für das Vorsteuerventil in etwa einer zeitlichen Ableitung des Förderstrom-Istwertes entspricht, kann es zur Verbesserung des Zeitverhaltens in Bremsphasen eingesetzt werden.According to the invention, the control electronics, starting from a drive signal for a pilot valve of the pressure medium source forms an actuating signal for the brake valve. Since the control signal for the pilot valve corresponds approximately to a time derivative of the flow rate actual value, it can be used to improve the time response in braking phases.

Nachfolgend wird die vorliegende Erfindung und deren Vorteile unter Bezugnahme auf das in der einzigen Figur dargestellte Ausführungsbeispiel näher erläutert.

  • Figur 1 zeigt eine hydraulische Steueranordnung zur Ansteuerung eines Verbrauchers mittels einer Verstellpumpe und eines elektromechanisch willkürlich ansteuerbaren Bremsventils.
Hereinafter, the present invention and its advantages will be explained in more detail with reference to the embodiment shown in the single FIGURE.
  • FIG. 1 shows a hydraulic control arrangement for controlling a consumer by means of a variable displacement pump and an electromechanically arbitrarily controllable brake valve.

Gemäß Figur 1 ist die hydraulische Steueranordnung 1 zur Ansteuerung eines hydraulischen Verbrauchers 2 mit einer Verstellpumpe 5, einem 4/2-Wege-Schaltventil 7 zur Einstellung der Bewegungsrichtung des Verbrauchers 2 und mit einem Bremsventil 9 ausgestattet. Das Bremsventil 9 ist in der Druckmittelleitung zwischen dem Verbraucher 2 und dem Druckmitteltank 3 angeordnet und als stetig verstellbares 2/2-Wegeventil ausgeführt. Durch einen Proportionalmagneten 10 wird das Bremsventil 9 betätigt.According to FIG. 1 is the hydraulic control assembly 1 for controlling a hydraulic consumer 2 with a variable displacement pump 5, a 4/2-way switching valve 7 for adjusting the direction of movement of the consumer 2 and equipped with a brake valve 9. The brake valve 9 is arranged in the pressure medium line between the consumer 2 and the pressure medium tank 3 and designed as a continuously adjustable 2/2-way valve. By a proportional solenoid 10, the brake valve 9 is actuated.

Als Verstellpumpe 5 kommt eine Schrägscheiben-Axialkolbenmaschine zum Einsatz. Über den Stellkolben 12 wird der Schwenkwinkel der Schrägscheibe und damit das Schöpfvolumen der Verstellpumpe 5 eingestellt. Ein Federelement 13 sorgt für eine Auslenkung der Schrägscheibe im drucklosen Zustand. Den Schwenkwinkel erfasst ein Schwenkwinkelsensor 14. Der Schwenkwinkel ist ein Maß für das Schöpfvolumen der Pumpe und auch für deren Förderstrom, wenn man von einer gleichbleibenden Antriebsdrehzahl ausgeht. Der Stellkolben 12 wird über ein Vorsteuerventil 16 angesteuert. Das Vorsteuerventil 16 ist als Stetigventil ausgeführt und mit einem Proportionalmagneten 17 und einem eigenen Wegsensor 18 zur Erfassung der Ventilposition ausgestattet. Stromabwärts des Ausgangsanschlusses der Verstellpumpe 5 ist ein Drucksensor 20 angeordnet, um den Ausgangsdruck der Verstellpumpe 5 zu erfassen.As a variable displacement pump 5, a swash plate axial piston machine is used. About the actuating piston 12, the pivot angle of the swash plate and thus the scoop volume of the variable 5 is set. A spring element 13 ensures a deflection of the swash plate in the unpressurized state. The swivel angle detects a swivel angle sensor 14. The swivel angle is a measure of the pumping volume of the pump and also for the flow rate, if one assumes a constant drive speed. The actuating piston 12 is controlled via a pilot valve 16. The pilot valve 16 is designed as a continuous valve and equipped with a proportional solenoid 17 and a separate displacement sensor 18 for detecting the valve position. Downstream of the output terminal of the variable displacement pump 5, a pressure sensor 20 is arranged to detect the output pressure of the variable displacement pump 5.

Eine Regel- und Steuerelektronik 25 umfasst eine Pumpenreglerkomponente 26 sowie eine Bremsventilsteuerkomponente 28. Die Pumpenreglerkomponente 26 sowie die Bremsventilsteuerkomponente 28 sind in einem gemeinsamen Gehäuse (nicht dargestellt) untergebracht. Der Pumpenreglerkomponente 26 sind die Istwert-Signale des Drucksensors 20, des Schwenkwinkelsensors 14, des Wegsensors 18 und ein an einem Eingangsanschluss 30 anliegender Druck-Sollwert und/oder ein Volumenstrom-Sollwert zugeführt. In an sich bekannter Weise regelt die Pumpenreglerkomponente 26 den Schwenkwinkel der Verstellpumpe 5 anhand der ihr zugeführten Istwertsignale und Sollwertsignale. Die Pumpenreglerkomponente 26 besitzt unter anderem einen Regler für den Ausgangsdruck sowie einen Regler für die Fördermenge. Bei gleichzeitiger Vorgabe eines Drucksollwerts sowie eines Förderstromsollwerts wird eine der beiden Größen Druck oder Förderstrom exakt ausgeregelt, während der Istwert der anderen Größe unter dem Sollwert gehalten wird. Außerdem kann auch die abgegebene Leistung als Regelgröße verwendet werden. Diese Regelmechanismen sind in dem bereits genannten Datenblatt RD 30630/06.06 beschrieben und werden daher nicht nochmals erläutert.A regulation and control electronics 25 includes a pump regulator component 26 and a brake valve control component 28. The pump regulator component 26 and the brake valve control component 28 are housed in a common housing (not shown). The pump control component 26 is supplied with the actual value signals of the pressure sensor 20, the swivel angle sensor 14, the displacement sensor 18 and a pressure setpoint value applied to an input connection 30 and / or a volumetric flow setpoint value. In a manner known per se, the pump regulator component 26 regulates the swivel angle of the variable displacement pump 5 on the basis of the actual value signals and setpoint signals supplied to it. The pump regulator component 26 has inter alia a regulator for the output pressure and a regulator for the flow rate. When simultaneously presetting a pressure setpoint and a flow rate setpoint, one of the two variables pressure or flow is precisely controlled, while the actual value of the other variable is kept below the setpoint. In addition, the output power can also be used as a controlled variable. These control mechanisms are described in the already mentioned data sheet RE 30630 / 06.06 and will therefore not be explained again.

Die Bremsventilsteuerkomponente 28 erhält zumindest eines der folgenden Eingangssignale: den Druck-Istwert, den Schwenkwinkel-Istwert, den Sollwert für Druck bzw. Förderstrom. Es können selbstverständlich auch mehrere der genannten Istwerte oder Sollwerte in Kombination als Eingangssignale der Bremsventilsteuerkomponente 28 herangezogen werden. Zusätzlich kann von der Pumpenreglerkomponente 26 ein Signal 32 zur Verfügung gestellt werden, das angibt, welche der Größen - Druck, Förderstrom oder Leistung - derzeit ausgeregelt wird.The brake valve control component 28 receives at least one of the following input signals: the actual pressure value, the actual swivel angle value, the desired value for pressure or delivery flow. It is of course also possible to use a plurality of said actual values or desired values in combination as input signals of the brake valve control component 28. In addition, the pump controller component 26 can provide a signal 32 which indicates which of the variables-pressure, flow or power-is currently being regulated.

In Analogie zur herkömmlichen Ansteuerung von Bremsventilen, wie sie im Datenblatt RD 64 298/09.97 beschrieben ist, kann der am Sensor 20 erfasste Druck als Steuergröße zur Ansteuerung des Regelventils 9 benutzt werden. Dazu wird durch die Bremsventilsteuerkomponente 28 z.B. unterhalb einer bestimmten Druckschwelle ein zum Ausgangsdruck der Verstellpumpe 5 invers proportionaler Betätigungsstrom für den Proportionalmagneten 10 erzeugt. Vorteilhaft ist hierbei, dass die Steuerkennlinie elektronisch beeinflusst und sehr einfach angepasst werden kann. So können unerwünschte Schwingungen beim Bremsvorgang durch eine passende Bedämpfung oder durch einen frequenzselektiven Filter vermieden werden. Der Druck-Istwert kann einer zeitlichen Ableitung unterzogen werden und der abgeleitete Druck-Istwert als Steuersignal für das Bremsventil verwendet werden. Dabei wird das Bremsventil nur bei einem Druckrückgang betätigt. Dadurch lässt sich ein stabileres Steuerverhalten sowie eine Energieeinsparung für den Pumpenantrieb erzielen.In analogy to the conventional control of brake valves, as described in the data sheet RD 64 298 / 09.97, the pressure detected at the sensor 20 can be used as a control variable for controlling the control valve 9. To do so, the brake valve control component 28 applies e.g. below a certain pressure threshold a to the output pressure of the variable displacement pump 5 inversely proportional actuation current for the proportional magnet 10 is generated. It is advantageous here that the control characteristic can be influenced electronically and adapted very easily. Thus, unwanted vibrations during braking can be avoided by a suitable damping or by a frequency-selective filter. The actual pressure value can be subjected to a time derivation and the derived pressure actual value can be used as a control signal for the brake valve. The brake valve is actuated only at a pressure drop. This allows a more stable control behavior and energy savings for the pump drive can be achieved.

In ähnlicher Weise lassen sich auch der Schwenkwinkel - als Maß für den Förderstrom-Istwert - oder dessen zeitliche Ableitung zur Ansteuerung des Bremsventils 9 durch die Bremsventilsteuerkomponente 28 verwenden. Die Geschwindigkeit des Verbrauchers 2 ist bei Beschleunigungsphasen und Fahrten mit konstanter Geschwindigkeit weitgehend proportional zum Schwenkwinkel. Durch die Ansteuerung des Bremsventils 9 mit einem Steuerstrom proportional der zeitlichen Ableitung des Schwenkwinkelsignals lässt sich eine schnelle Reaktion des Verbrauchers auf eine Schwenkwinkelrücknahme - also in den Bremsphasen - erzielen. Die Geschwindigkeit des Verbrauchers folgt damit auch bei einer Förderstromreduzierung dem vorgegebenen Förderstromprofil. Bei der Ansteuerung der hydraulischen Steueranordnung 1 mit einem Förderstrom-Sollwert am Eingangsanschluss 30 kann somit in allen Betriebszuständen, in denen der Verbraucher frei oder gegen eine Last verfahrbar ist, von der Übereinstimmung zwischen der Geschwindigkeit des Verbrauchers und dem Förderstrom-Istwert ausgegangen werden. Dies vereinfacht die Ansteuerung der hydraulischen Steueranordnung.Similarly, the swivel angle - as a measure of the actual flow - or its time derivative for controlling the brake valve 9 can be used by the brake valve control component 28. The speed of the load 2 is largely proportional to the swing angle during acceleration and constant speed travel. By controlling the brake valve 9 with a control current proportional to the time derivative of the swivel angle signal can be a quick reaction of the consumer to a swivel angle return - ie in the braking phases - achieve. The speed of the consumer thus follows even with a flow reduction, the predetermined flow profile. When driving the hydraulic control arrangement 1 with a flow rate setpoint at the input port 30 can thus be assumed in all operating conditions in which the consumer is free or movable against a load of the correspondence between the speed of the consumer and the flow rate actual value. This simplifies the control of the hydraulic control arrangement.

Als weitere Vereinfachung kann auch der Förderstrom-Sollwert oder dessen zeitliche Ableitung zur Ansteuerung des Bremsventils 9 verwendet werden.As a further simplification, it is also possible to use the flow rate set value or its time derivative for triggering the brake valve 9.

Dadurch wird die Ansteuerung des Bremsventils 9 rückkopplungsfrei. Die Reaktionsgeschwindigkeit der Ansteuerung des Bremsventils 9 kann deutlich erhöht werden. Ein Regelverzögerung zwischen dem Sollwerteingang 30 und den an den Sensoren 14 und 20 gemessenen Istwertsignalen wirkt sich nicht auf die Ansteuerung des Bremsventils aus. Es sind sehr schnelle und kräftige Bremsvorgänge möglich. Durch den beim Bremsvorgang aufgebauten Gegendruck, der auf den Ausgang der Verstellpumpe 5 zurückwirkt, wird ein Rückstellvorgang der Verstellpumpe 5 beschleunigt.As a result, the control of the brake valve 9 is feedback-free. The reaction rate of the control of the brake valve 9 can be significantly increased. A control delay between the setpoint input 30 and the actual value signals measured at the sensors 14 and 20 does not affect the activation of the brake valve. Very fast and powerful braking is possible. Due to the backpressure built up during the braking process, which acts back on the output of the variable displacement pump 5, a return operation of the variable displacement pump 5 is accelerated.

Eine rückkopplungsfreie Ansteuerung des Bremsventils 9 ist auch bei Verwendung des Druck-Sollsignals oder dessen Ableitung gewährleistet.A feedback-free control of the brake valve 9 is ensured even when using the desired pressure signal or its derivative.

Es kann vorteilhaft sein, die Ansteuerung des Bremsventils 9 anhand der aktiven Regelgröße der Pumpenreglerkomponente 26, welche durch das Signal 32 mitgeteilt wird, vorzunehmen. Unter Ausnutzung des Signals 32 kann z.B. in einer Druckregelphase durch Stellen des Bremsventils 9 in eine Drosselstellung ein Durchgehen des Verbraucher bei Wegbrechen einer Gegenkraft verhindert werden. Beim Verfahren des Verbrauchers 2 in Förderstromregelung und unter geringer Last kann das Bremsventil zur Minimierung des Energieverbrauchs vollständig geöffnet sein. Es kann aber auch mittels des Bremsventils 9 ein gewisser, am Drucksensor 20 erfassbarer Mindest-Gegendruck eingestellt werden, um den Einfluss von Störgrößen auf die Bewegung des Verbrauchers zu vermindern und um eine hohe Proportionalität zwischen dem Schwenkwinkelsignal und der Geschwindigkeit des Verbrauchers 2 zu gewährleisten.It may be advantageous to carry out the control of the brake valve 9 on the basis of the active controlled variable of the pump regulator component 26, which is communicated by the signal 32. Using signal 32, e.g. in a pressure control phase by setting the brake valve 9 in a throttle position a passage of the consumer can be prevented when breaking away a counterforce. In the process of the consumer 2 in flow control and under light load, the brake valve to minimize the energy consumption can be fully opened. But it can also be adjusted by means of the brake valve 9, a certain detectable at the pressure sensor 20 minimum backpressure to reduce the influence of disturbances on the movement of the consumer and to ensure a high degree of proportionality between the swivel angle signal and the speed of the consumer 2.

Als Verbraucher 2 können lineare Stellglieder wie hydraulische Kolben-ZylinderEinheiten oder aber hydraulische Rotationsmaschinen zum Einsatz kommen. Die Verstellpumpe 5 kann anstelle einer Axialkolbenpumpe in Schrägscheibenbauweise sämtliche bekannten einer Druck- oder Förderstromregelung zugänglichen verstellbaren Hydromaschinen umfassen, z.B. Axialkoibenpumpen in Schrägachsenbauweise, Flügelzellenpumpen oder Radialkolbenpumpen.As consumer 2 linear actuators such as hydraulic piston-cylinder units or hydraulic rotary machines can be used. The variable displacement pump 5 may comprise, instead of a swash plate type axial piston pump, all known variable displacement hydraulic machines accessible to pressure or flow control, e.g. Axialkoibenpumpen in Schrägachsenbauweise, vane pumps or radial piston pumps.

Die Pumpenreglerkomponente 26 und die Bremsventilsteuerkomponente 28 können in analoger Schaltungstechnik oder besonders vorteilhaft als Programmmodule eines Regel-/Steuerprogramms eines Mikrokontrollers ausgebildet sein. Durch die ohnehin vorhandenen Eingangssignale - den Signalen der Sensoren 14 und 20 und den Sollwertsignalen - erschöpft sich der zusätzliche Hardwareaufwand in einer zusätzlichen zur Ansteuerung des Proportionalmagneten 10 benötigten Verstärkerstufe. Die Verstärkerstufe kann z.B. auf dem Ventil montiert sein. In der Regel- und Steuerelektronik 25 wird dann im Vergleich zu einer herkömmlichen Pumpenregelelektronik keine zusätzliche Hardware benötigt.The pump regulator component 26 and the brake valve control component 28 can be implemented in analog circuit technology or particularly advantageously as program modules of a control / control program of a microcontroller be educated. Due to the already existing input signals - the signals of the sensors 14 and 20 and the setpoint signals - the additional hardware effort is exhausted in an additional amplifier stage 10 required for driving the proportional magnet 10. The amplifier stage can be mounted on the valve, for example. In the control electronics 25 and then no additional hardware is required compared to a conventional pump control electronics.

Gemäß einer sehr einfachen Ausführung wäre es auch möglich, ausgehend von dem Ansteuersignal für das Vorsteuerventil 16 der Verstellpumpe 5 das Ansteuersignal für das Bremsventils 9 zu beeinflussen. Da das Vorsteuerventil 16 immer dann angesteuert wird, wenn die Fördermenge geändert werden soll, entspricht dieses Signal in etwa einer zeitlichen Ableitung des Förderstrom-Istwerts.According to a very simple embodiment, it would also be possible, starting from the drive signal for the pilot valve 16 of the variable displacement pump 5, to influence the drive signal for the brake valve 9. Since the pilot valve 16 is always activated when the flow rate is to be changed, this signal corresponds approximately to a time derivative of the flow rate actual value.

Weiter ist es möglich, das Bremsventil im Rahmen einer Regelung anzusteuern. Dabei kann z.B. der durch das Bremsventil aufgestaute Druck über einen eigenen Drucksensor oder über den Drucksensor 20 erfasst und als Regelgröße verwendet werden. Für eine sehr einfachere Ansteuerung der Verstellpumpe 5 könnte diese auch ohne eine elektrische Druckrückführung oder Schwenkwinkelrückführung betrieben werden, und z.B. nur über eine hydrostatische Druckrückführung an den Stellkolben 12 oder ein ähnliches Stellglied verfügen.Further, it is possible to control the brake valve as part of a scheme. In this case, e.g. the pressure accumulated by the brake valve is detected via its own pressure sensor or via the pressure sensor 20 and used as a controlled variable. For a very simple control of the variable displacement pump 5, this could also be operated without an electrical pressure feedback or swivel angle feedback, and e.g. only have a hydrostatic pressure feedback to the actuator piston 12 or a similar actuator.

Bei der erfindungsgemäßen hydraulischen Steueranordnung zur Steuerung eines Verbrauchers mittels einer verstellbaren Druckmittelquelle und einem Bremsventil ist das Bremsventil durch eine elektromechanische Betätigungsvorrichtung willkürlich ansteuerbar. Dies ermöglicht es, das Bremsventil durch robuste und einfach konfigurierbare elektronische Regel- oder Steuermechanismen anzusteuern. Zudem kann eine Ansteuerung mit nur geringem Aufwand durch die Steuerelektronik der verstellbaren Druckmittelquelle erfolgen.In the hydraulic control arrangement according to the invention for controlling a consumer by means of an adjustable pressure medium source and a brake valve, the brake valve can be controlled arbitrarily by an electromechanical actuator. This makes it possible to control the brake valve by robust and easily configurable electronic control or regulating mechanisms. In addition, a control can be done with little effort by the control electronics of the adjustable pressure medium source.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Hydraulische SteueranordnungHydraulic control arrangement
22
Verbraucherconsumer
33
DruckmitteltankPressure tank
55
Verstellpumpevariable
77
Schaltventilswitching valve
99
Bremsventilbrake valve
1010
Proportionalmagnetproportional solenoid
1212
Stellkolbenactuating piston
1313
Federelementspring element
1414
SchwenkwinkelsensorSwing angle sensor
1616
Vorsteuerventilpilot valve
1717
Proportionalmagnetproportional solenoid
1818
Wegsensordisplacement sensor
2020
Drucksensorpressure sensor
2525
Regel- und SteuerelektronikControl electronics
2626
PumpenreglerkomponentePump regulator component
2828
BremsventilsteuerkomponenteBrake valve engine
3030
SollwerteingangSetpoint input
3232
RegelgrößensignalControlled variable signal

Claims (8)

  1. Hydraulic control device with an adjustable pressure-medium source (5) for activating a hydraulic consumer (2) with a pressure medium, with control electronics (25) for activating an actuating member (12, 16) of the pressure-medium source (5) and with a brake valve (9), by means of which a hydraulic connection between the consumer (2) and a pressure-medium tank (3) can be throttled, the brake valve (9) being arbitrarily activatable by means of an electromechanical actuation device (10), characterized in that the control electronics (25) automatically select pressure regulation or volumetric-flow regulation of the pressure-medium source (5) and form the actuation signal for the brake valve (9) as a function of the selected regulating mechanism, or in that the control electronics (25) form the actuation signal for the brake valve (9) on the basis of an activation signal for a pilot control valve (16) of the pressure-medium source (5).
  2. Hydraulic control device according to Claim 1, characterized in that the electromechanical actuation device (10) is a proportional magnet.
  3. Hydraulic control device according to Claim 1 or 2, characterized in that the control electronics (25) are connected to the actuation device (10) of the brake valve (9).
  4. Hydraulic control device according to one of Claims 1 to 3, characterized in that the control electronics (25) detect a pressure actual value and/or a volumetric-flow actual value of the pressure-medium source (5) and on the basis of this form an actuation signal for the brake valve (9).
  5. Hydraulic control device according to Claim 4, characterized in that the control electronics (25) form the actuation signal on the basis of a time derivation of the pressure actual value or of the volumetric-flow actual value.
  6. Hydraulic control device according to one of Claims 1 to 5, characterized in that the control electronics (25) form the actuation signal for the brake valve (9) on the basis of a pressure desired value (30), supplied to them, and/or volumetric-flow desired value (30), supplied to them, of the pressure-medium source (5).
  7. Hydraulic control device according to one of Claims 1 to 6, characterized in that the control electronics comprise a pump regulator component (26) for regulating a variable-displacement pump and a brake-valve activation component (28) for activating the brake valve (9), and in that both components (26, 28) are arranged in a common housing.
  8. Hydraulic control device according to Claim 7, characterized in that the housing is arranged on the variable-displacement pump.
EP20070022458 2006-12-06 2007-11-20 Hydraulic control device Not-in-force EP1930604B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200610057475 DE102006057475A1 (en) 2006-12-06 2006-12-06 Hydraulic control arrangement

Publications (3)

Publication Number Publication Date
EP1930604A2 EP1930604A2 (en) 2008-06-11
EP1930604A3 EP1930604A3 (en) 2012-03-28
EP1930604B1 true EP1930604B1 (en) 2013-05-15

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ID=39153990

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070022458 Not-in-force EP1930604B1 (en) 2006-12-06 2007-11-20 Hydraulic control device

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EP (1) EP1930604B1 (en)
DE (1) DE102006057475A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020213262A1 (en) 2020-10-21 2022-04-21 Robert Bosch Gesellschaft mit beschränkter Haftung Method for operating a hydraulic drive

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013165951A1 (en) * 2012-04-30 2013-11-07 Parker-Hannifin Corporation Operator commanded hydraulic pump flow
DE102014222326B4 (en) * 2014-10-31 2016-06-09 Tadano Faun Gmbh hydraulic arrangement

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19950910B4 (en) * 1999-10-22 2010-11-04 Bosch Rexroth Aktiengesellschaft Hydraulic drive system and hydraulic 4/3-way valve usable therein
US6715402B2 (en) * 2002-02-26 2004-04-06 Husco International, Inc. Hydraulic control circuit for operating a split actuator mechanical mechanism
US6779340B2 (en) * 2002-09-25 2004-08-24 Husco International, Inc. Method of sharing flow of fluid among multiple hydraulic functions in a velocity based control system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020213262A1 (en) 2020-10-21 2022-04-21 Robert Bosch Gesellschaft mit beschränkter Haftung Method for operating a hydraulic drive
EP3988801A1 (en) 2020-10-21 2022-04-27 Robert Bosch GmbH Method for operating a hydraulic drive

Also Published As

Publication number Publication date
DE102006057475A1 (en) 2008-06-12
EP1930604A3 (en) 2012-03-28
EP1930604A2 (en) 2008-06-11

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