EP1686268A2 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
EP1686268A2
EP1686268A2 EP05019936A EP05019936A EP1686268A2 EP 1686268 A2 EP1686268 A2 EP 1686268A2 EP 05019936 A EP05019936 A EP 05019936A EP 05019936 A EP05019936 A EP 05019936A EP 1686268 A2 EP1686268 A2 EP 1686268A2
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control device
hydraulic control
pressure source
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
EP05019936A
Other languages
German (de)
French (fr)
Other versions
EP1686268B1 (en
EP1686268A3 (en
Inventor
Martin Dipl.-Ing. Heusser
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.)
Hawe Hydraulik SE
Original Assignee
Hawe Hydraulik SE
Hawe Hydraulik GmbH and Co KG
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Publication of EP1686268A2 publication Critical patent/EP1686268A2/en
Publication of EP1686268A3 publication Critical patent/EP1686268A3/en
Application granted granted Critical
Publication of EP1686268B1 publication Critical patent/EP1686268B1/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check valves
    • 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
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • 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
    • F15B2211/615—Filtering means
    • 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
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8755—Emergency shut-down

Definitions

  • the invention relates to a hydraulic control device specified in the preamble of claim 1 Art.
  • Such hydraulic control devices are used, for example, in stationary cranes or mobile cranes and in other hoists with multiple components to be moved in order to control the working speed and direction of at least one hydraulic consumer via the directional control valve.
  • a pressure source e.g. a control pump
  • the flow rate is adjusted by means of the load pressure-dependent control pressure in the load pressure control circuit to the respective needs.
  • a regulating pump feeds a base pressure between 15 and 30 bar, even in a regulated state.
  • the basic pressure may still be sufficient to adjust over the directional control valve, the hydraulic consumer, which can lead to a dangerous situation.
  • a hydraulic control device includes in the emergency stop shutdown system designed as a 3/2-slide solenoid switching valve emergency stop valve, which is connected to the load pressure control circuit and the pressure signal that provides an isolation valve between a passage position and a shut-off adjusted.
  • the isolation valve is a 5/2-way valve between the pressure source and the supply line and also monitors the connection of the load pressure control circuit to the pressure source, eg the control connection of the control pump.
  • the emergency stop solenoid switching valve is energized so that it holds the isolation valve in the passage position in which the pressure source to the supply line and the load pressure control circuit are connected to the control port.
  • the emergency stop solenoid valve In emergency stop, the emergency stop solenoid valve is de-energized to relieve the pilot pressure of the isolation valve to the return, so that the isolation valve goes to the shut-off position by its spring and disconnects the pressure source from the supply line and relieves the control port to the return.
  • the spring chamber of the separating valve is constantly connected to the return, so that the separating valve does not switch unintentionally or reliably remains in the passage position during normal operation.
  • the well-known emergency stop system is complex, builds big and is expensive.
  • the maximum flow rate is independent of pressure limits.
  • the invention has for its object to form a hydraulic control device of the type mentioned with a cost-effective, structurally simple and functionally reliable emergency stop shutdown system.
  • the two 2/2-way valves are structurally simple, inexpensive and compact.
  • the isolation valve In normal operation, the isolation valve is not held by the emergency stop solenoid valve in the passage position, but on the basis of the delivery pressure of the pressure source derived pilot pressure.
  • the emergency stop solenoid valve is energized in normal operation and in the shut-off position, so that the pilot pressure, which acts on the isolation valve to the passage position, only has to overcome the force of the spring of the isolation valve.
  • the permanent connection of the spring chamber to the return prevents the isolation valve from accidentally shutting off or throttling.
  • the emergency stop solenoid valve In emergency stop the emergency stop solenoid valve is de-energized and switched to its passage position, so that the then acting parallel to the spring control pressure reliably adjusts the shut-off position of the separating valve and holds.
  • the diaphragm device between the spring chamber and the return allows a permanent discharge of pressure medium, without endangering the shut-off position of the separating valve. In a recent switch to normal operation can be avoided by the diaphragm device, an undesirable sudden sudden switching (pressure surge) of the isolation valve.
  • the diaphragm device may include a nozzle.
  • the aperture device a two-way flow regulator, the pressure-independent setting a predetermined pressure medium rate, thus ensuring a uniform switching behavior.
  • the two-way flow regulator improves operational safety, because the predetermined pressure medium rate can be matched exactly to the operating conditions of the hydraulic control device. It may be useful if the two-way current controller is adjustable.
  • the pressure medium rate is set to about 0.3 to 0.5 l / min.
  • a commercially available, available in various specifications lowering brake valve preferably even a screw-Senkbremsventil used for cost reasons as a two-way flow regulator.
  • the lowering brake valve may include an inlet side movable against the force of a spring orifice piston with at least one smaller inlet aperture and at least one larger drain aperture. With the drain aperture, a stationary control edge acts in such a way that the outflow cross section from the drain aperture is continuously reduced with increasing inlet pressure. In this way, the same pressure medium rate is always set pressure-independent.
  • the emergency stop shutdown system is expediently used when the pressure source is a regulating pump controlled from the load pressure control circuit.
  • the control pressure for the control pump can either be held or relieved in any way to return.
  • the pressure source could also be a constant-displacement pump, which, for example, cooperates with a non-pressurized circulation system or is switched off in the event of an emergency stop.
  • a hydraulic control device S in Fig. 1 is used with a pressure source P and a return R via a multi-way control valve W for direction and speed control of at least one hydraulic consumer V.
  • the pressure source P is for example a control pump, with a control connection LS.
  • the pressure source P could be a constant pump, which is combined, for example, with a pressure-free circulating system, which is controlled via the control connection LS.
  • a pressureless circulation system could also be associated with the control pump 8.
  • an emergency stop system N is contained, for example in a single housing block, on or in which the individual components are combined.
  • the pressure source P is connected to a pressure line 1, which can be connected by a separating valve T optionally with a supply line 2 or disconnected therefrom.
  • the supply line 2 leads to the at least one multi-way control valve W, which is connected to a return line 3 to the return R.
  • a return line 4 is also connected to the return R.
  • Pressure limiting valves 5 between the pressure line 1 and the return line 4 limit the system pressure.
  • control lines 7, 8 to the separating valve T (a 2/2-way valve with pressure pilot 9 against the force of a spring 14).
  • the control line 7 leads to the pressure pilot control 9 of the separating valve T, with which the separating valve T from the shut-off position shown in the passage position can be switched (pressure line 1 connected to the supply line 2).
  • an emergency stop solenoid valve M is provided between the branch 6 and a spring chamber 10 of the separating valve T, expediently a 2/2-solenoid switching valve by a switching magnet 12 from the set by a spring 11 passage position in a Locking position is adjustable (possibly with pressure pre-control).
  • a discharge line 17 leads via a filter 15 to a diaphragm device B, for example a two-way flow regulator 16, which is connected on the output side via a discharge line 17 'to the return line 4.
  • the diaphragm device B is in the simplest case a nozzle. However, the preference is given to a two-way flow regulator 16 which maintains a predetermined pressure medium rate independently of pressure.
  • Part of the hydraulic control device S may further be a load pressure control circuit L, which leads in the input section E to the port LS, in which case a hydraulic damping device D is provided, consisting of a Dämpfdrossel 20 and two mutually opposite check valves 18, 19 and a throttle 21 exists.
  • a hydraulic damping device D consisting of a Dämpfdrossel 20 and two mutually opposite check valves 18, 19 and a throttle 21 exists.
  • a 2/2-solenoid switching valve 23 may be provided to relieve the control pressure at the port LS, for example, in emergency stop, wanted to return R.
  • the emergency-off solenoid switching valve M is energized and in the shut-off position, so that the spring chamber 10 of the separating valve T receives no control pressure from the control line 8.
  • the isolation valve T is provided by the control pressure in the control line 7 on the pilot side 9 in the passage position and held in this, so that the pressure line 1 is connected to the supply line 2.
  • the spring chamber 10 is relieved via the diaphragm device B to the return.
  • the 2/2-solenoid switching valve 23 is also energized and in the shut-off, so that at the port LS load pressure-dependent control pressure prevails, with the example, the delivery rate of the pressure source P is adapted to the needs.
  • the emergency-off solenoid switching valve M is de-energized if the multi-way control valve W is still deflected, and is displaced by the spring 11 into the passage position (FIG. 1).
  • the spring chamber 10 receives via the control line 8 control pressure, so that the separating valve T is adjusted by this control pressure and the force of the spring 14 in the shut-off position and held in this.
  • the diaphragm device B i. the two-way flow regulator 16, allows only a predetermined pressure medium rate to flow, for example between 0.3 and 0.5 l / min, so that the separating valve T remains in the shut-off position and yet in the spring chamber 10 in addition to the force of the spring 14 only a predetermined Pressure prevails.
  • the 2/2-solenoid switching valve 23 can also be de-energized, and take the passage position, so that the control pressure at the port LS to return R is reduced.
  • Fig. 2 illustrates a block diagram of the embodiment of the two-way flow regulator 16 of FIG. 1, which is arranged between the spring chamber 10 and the return R.
  • the two-way flow regulator 16 has a smaller inlet aperture 24 in the drain line 17.
  • a control line 25 branches to the closing side of a 2/2 control valve 27 from.
  • a further control line 26 branches off to the control side of the 2/2 control valve, at which a control spring 33 also acts.
  • This two-way flow regulator 16 can be formed by various hydraulic components, or is expediently a commercial Senkbremsventil SB of FIG. 3, which is designed here as a screw-Senkbremsventil.
  • the lowering brake valve SB has an outer screw-in housing 28 with a rotary handle 29, an external thread 30 and a peripheral seal 31.
  • a stationary control edge 37 is formed in the outer housing 28, where the drain line 17 is connected.
  • a diaphragm piston 32 is slidably guided, which is loaded by the control spring 33 in the direction of a stop 39.
  • the control spring 33 is supported in the outer housing 28 on a spring abutment 38.
  • the drain line 17 from the spring chamber 10 opens in the upper open end of the outer housing 28, i. where the orifice piston 32 has at least the smaller inlet orifice 24. Further, in the orifice piston 32 at least one drain aperture 36 is formed, which cooperates with the control edge 37.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The device has a separation valve (T) with a spring chamber (10) associated with a rear flow. A magnetic control valve (M) is a 2/2-way valve and arranged between a pressure source (P) and the chamber. The separation valve is a 2/2-way valve, whose pressure pre-control side is permanently connected with the source and provided for adjusting a passage condition. A blending device is provided between the chamber and the rear flow.

Description

Die Erfindung betrifft eine hydraulische Steuervorrichtung der im Oberbegriff des Anspruchs 1 angegebenen Art.The invention relates to a hydraulic control device specified in the preamble of claim 1 Art.

Derartige hydraulische Steuervorrichtungen werden beispielsweise in stationären Kränen oder Mobilkränen und bei anderen Hebezeugen mit mehreren zu bewegenden Komponenten verwendet, um Arbeitsgeschwindigkeit und Richtung zumindest eines Hydroverbrauchers über das Wegesteuerventil zu steuern. Als Druckquelle dient z.B. eine Regelpumpe, deren Fördermenge mittels des lastdruckabhängigen Steuerdrucks im Lastdrucksteuerkreis an den jeweiligen Bedarf angepasst wird. Eine Regelpumpe speist jedoch selbst in abgeregeltem Zustand einen Grunddruck zwischen 15 und 30 Bar ein. Bei einer Not-Aus-Betätigung der Steuervorrichtung wird zwar bei noch verstelltem Wegesteuerventil die Regelpumpe abgeregelt; der Grunddruck kann jedoch noch ausreichen, um über das Wegesteuerventil den Hydroverbraucher zu verstellen, was zu einer Gefahrensituation führen kann.Such hydraulic control devices are used, for example, in stationary cranes or mobile cranes and in other hoists with multiple components to be moved in order to control the working speed and direction of at least one hydraulic consumer via the directional control valve. As a pressure source, e.g. a control pump, the flow rate is adjusted by means of the load pressure-dependent control pressure in the load pressure control circuit to the respective needs. However, a regulating pump feeds a base pressure between 15 and 30 bar, even in a regulated state. In an emergency stop operation of the control device while the control pump is still adjusted when the directional control valve is still adjusted; However, the basic pressure may still be sufficient to adjust over the directional control valve, the hydraulic consumer, which can lead to a dangerous situation.

Die aus DE 43 24 717 A bekannte hydraulische Steuervorrichtung enthält im Not-Aus-Abschaltsystem das als 3/2-Schieber-Magnetschaltventil ausgebildete Not-Aus-Ventil, das an den Lastdruck-Steuerkreis angeschlossen ist und das Drucksignal liefert, das ein Trennventil zwischen einer Durchgangsstellung und einer Absperrstellung verstellt. Das Trennventil ist ein 5/2-Wegeventil zwischen der Druckquelle und der Versorgungsleitung und überwacht auch die Verbindung des Lastdruck-Steuerkreises mit der Druckquelle, z.B. dem Regelanschluss der Regelpumpe. Im Normalbetrieb ist das Not-Aus-Magnetschaltventil bestromt, so dass es das Trennventil in der Durchgangsstellung hält, in der die Druckquelle mit der Versorgungsleitung und der Lastdruck-Steuerkreis mit dem Regelanschluss verbunden sind. Bei Not-Aus wird das Not-Aus-Magnetschaltventil entregt, um den Vorsteuerdruck des Trennventils zum Rücklauf zu entlasten, so dass das Trennventil durch seine Feder in die Absperrstellung geht und die Druckquelle von der Versorgungsleitung trennt und den Regelanschluss zum Rücklauf entlastet. Dabei ist die Federkammer des Trennventils ständig mit dem Rücklauf verbunden, damit das Trennventil nicht ungewollt schaltet bzw. bei Normalbetrieb zuverlässig in der Durchgangsstellung bleibt. Das bekannte Not-Aus-Abschaltsystem ist aufwendig, baut groß und ist teuer. Außerdem wird ggfs. die maximale Fördermenge druckunabhängig begrenzt.The well-known from DE 43 24 717 A hydraulic control device includes in the emergency stop shutdown system designed as a 3/2-slide solenoid switching valve emergency stop valve, which is connected to the load pressure control circuit and the pressure signal that provides an isolation valve between a passage position and a shut-off adjusted. The isolation valve is a 5/2-way valve between the pressure source and the supply line and also monitors the connection of the load pressure control circuit to the pressure source, eg the control connection of the control pump. In normal operation, the emergency stop solenoid switching valve is energized so that it holds the isolation valve in the passage position in which the pressure source to the supply line and the load pressure control circuit are connected to the control port. In emergency stop, the emergency stop solenoid valve is de-energized to relieve the pilot pressure of the isolation valve to the return, so that the isolation valve goes to the shut-off position by its spring and disconnects the pressure source from the supply line and relieves the control port to the return. In this case, the spring chamber of the separating valve is constantly connected to the return, so that the separating valve does not switch unintentionally or reliably remains in the passage position during normal operation. The well-known emergency stop system is complex, builds big and is expensive. In addition, if necessary, the maximum flow rate is independent of pressure limits.

Weiterer Stand der Technik ist enthalten in DE 199 04 616 A.Further prior art is contained in DE 199 04 616 A.

Der Erfindung liegt die Aufgabe zugrunde, eine hydraulische Steuervorrichtung der eingangs genannten Art mit einem kostengünstigen, baulich einfachen und funktionssicheren Not-Aus-Abschaltsystem auszubilden.The invention has for its object to form a hydraulic control device of the type mentioned with a cost-effective, structurally simple and functionally reliable emergency stop shutdown system.

Die gestellte Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst.The stated object is achieved with the features of claim 1.

Die beiden 2/2-Wegeventile (ein Magnetventil und ein gegen Federkraft druckvorgesteuertes Ventil) sind baulich einfach, kostengünstig und kompakt. Im Normalbetrieb wird das Trennventil nicht über das Not-Aus-Magnetschaltventil in der Durchgangsstellung gehalten, sondern über den vom Förderdruck der Druckquelle abgeleiteten Vorsteuerdruck. Das Not-Aus-Magnetschaltventil ist im Normalbetrieb bestromt und in der Absperrstellung, so dass der Vorsteuerdruck, der das Trennventil zur Durchgangsstellung beaufschlagt, nur die Kraft der Feder des Trennventils zu überwinden hat. Die permanente Verbindung der Federkammer zum Rücklauf verhindert, dass das Trennventil ungewollt absperrt oder abdrosselt. Bei Not-Aus wird das Not-Aus-Magnetschaltventil entregt und in seine Durchgangstellung geschaltet, so dass der dann parallel zur Feder wirkende Steuerdruck zuverlässig die Absperrstellung des Trennventils einstellt und hält. Die Blendeneinrichtung zwischen der Federkammer und dem Rücklauf ermöglicht einen permanenten Abfluss an Druckmittel, ohne die Absperrstellung des Trennventils zu gefährden. Bei einer neuerlichen Umschaltung in den Normalbetrieb kann durch die Blendeneinrichtung ein gegebenenfalls unerwünschtes schlagartiges Umschalten (Druckstoß) des Trennventils vermieden werden.The two 2/2-way valves (a solenoid valve and a spring-pressure-controlled valve) are structurally simple, inexpensive and compact. In normal operation, the isolation valve is not held by the emergency stop solenoid valve in the passage position, but on the basis of the delivery pressure of the pressure source derived pilot pressure. The emergency stop solenoid valve is energized in normal operation and in the shut-off position, so that the pilot pressure, which acts on the isolation valve to the passage position, only has to overcome the force of the spring of the isolation valve. The permanent connection of the spring chamber to the return prevents the isolation valve from accidentally shutting off or throttling. In emergency stop the emergency stop solenoid valve is de-energized and switched to its passage position, so that the then acting parallel to the spring control pressure reliably adjusts the shut-off position of the separating valve and holds. The diaphragm device between the spring chamber and the return allows a permanent discharge of pressure medium, without endangering the shut-off position of the separating valve. In a recent switch to normal operation can be avoided by the diaphragm device, an undesirable sudden sudden switching (pressure surge) of the isolation valve.

In einer einfachen Ausführungsform kann die Blendeneinrichtung eine Düse enthalten. Da jedoch eine Düse bei hohem Druck mehr Druckmittel abströmen lässt als bei niedrigerem Druck, wäre kein gleichbleibendes Umschaltverhalten des Trennventils sichergestellt. Deshalb ist bei einer zweckmäßigen Ausführungsform die Blendeneinrichtung ein Zweiwege-Stromregler, der druckunabhängig eine vorbestimmte Druckmittelrate einstellt und somit ein gleichförmiges Umschaltverhalten gewährleistet. Der Zweiwege-Stromregler verbessert die Betriebssicherheit, weil die vorbestimmte Druckmittelrate exakt auf die Betriebsbedingungen der hydraulischen Steuervorrichtung abgestimmt sein kann. Dabei kann es zweckmäßig sein, wenn der Zweiwege-Stromregler einstellbar ist.In a simple embodiment, the diaphragm device may include a nozzle. However, since a nozzle can discharge more pressure medium at high pressure than at lower pressure, no constant switching behavior of the separating valve would be ensured. Therefore, in an advantageous embodiment, the aperture device a two-way flow regulator, the pressure-independent setting a predetermined pressure medium rate, thus ensuring a uniform switching behavior. The two-way flow regulator improves operational safety, because the predetermined pressure medium rate can be matched exactly to the operating conditions of the hydraulic control device. It may be useful if the two-way current controller is adjustable.

Bei einer zweckmäßigen Ausführungsform wird die Druckmittelrate auf ca. 0,3 bis 0,5 l/min eingestellt.In an expedient embodiment, the pressure medium rate is set to about 0.3 to 0.5 l / min.

Bei einer weiteren zweckmäßigen Ausführungsform wird aus Kostengründen als Zweiwege-Stromregler ein handelsübliches, in verschiedenen Spezifikationen erhältliches Senkbremsventil, vorzugsweise sogar ein Einschraub-Senkbremsventil, verwendet.In a further advantageous embodiment, a commercially available, available in various specifications lowering brake valve, preferably even a screw-Senkbremsventil used for cost reasons as a two-way flow regulator.

Das Senkbremsventil kann einen zulaufseitig gegen die Kraft einer Feder verschiebbaren Blendenkolben mit wenigstens einer kleineren Zulaufblende und wenigstens einer größeren Ablaufblende enthalten. Mit der Ablaufblende wirkt eine stationäre Steuerkante derart zusammen, dass der Abströmquerschnitt aus der Ablaufblende mit steigendem Zulaufdruck stufenlos verringert wird. Auf diese Weise wird druckunabhängig stets die gleiche Druckmittelrate eingestellt.The lowering brake valve may include an inlet side movable against the force of a spring orifice piston with at least one smaller inlet aperture and at least one larger drain aperture. With the drain aperture, a stationary control edge acts in such a way that the outflow cross section from the drain aperture is continuously reduced with increasing inlet pressure. In this way, the same pressure medium rate is always set pressure-independent.

Das Not-Aus-Abschaltsystem wird zweckmäßig dann verwendet, wenn die Druckquelle eine aus dem Lastdruck-Steuerkreis geregelte Regelpumpe ist. In einer Not-Aus-Situation kann der Regeldruck für die Regelpumpe entweder gehalten oder auf beliebige Weise zum Rücklauf entlastet werden.The emergency stop shutdown system is expediently used when the pressure source is a regulating pump controlled from the load pressure control circuit. In an emergency stop situation, the control pressure for the control pump can either be held or relieved in any way to return.

Alternativ könnte die Druckquelle jedoch auch eine Konstantpumpe sein, die beispielsweise mit einem drucklosen Umlaufsystem kooperiert oder bei Not-Aus abgeschaltet wird.Alternatively, however, the pressure source could also be a constant-displacement pump, which, for example, cooperates with a non-pressurized circulation system or is switched off in the event of an emergency stop.

Um Schwingungen im System möglichst schnell abzudämpfen oder am Entstehen zu verhindern, ist es zweckmäßig, zwischen dem Lastdruck-Steuerkreis und dem Regelanschluss der Druckquelle eine hydraulische Dämpfvorrichtung vorzusehen.In order to damp vibrations in the system as quickly as possible or to prevent their occurrence, it is expedient to provide a hydraulic damping device between the load pressure control circuit and the control connection of the pressure source.

Schließlich wird zweckmäßig das gesamte Not-Aus-Abschaltsystem mit der Blendeneinrichtung in ein Eingangs-Sektions-Gehäuse eingegliedert, zweckmäßigerweise in ein Eingangs-Sektions-Gehäuse z.B. für eine Regelpumpe.Finally, it is convenient to incorporate the entire emergency stop system with the shutter in an input section housing, conveniently in an input section housing e.g. for a control pump.

Anhand der Zeichnung werden Ausführungsformen des Erfindungsgegenstandes erläutert. Es zeigen:

Fig. 1
ein Blockschaltbild einer Eingangs-Sektion einer hydraulischen Steuervorrichtung,
Fig. 2
ein in Fig. 1 symbolisch dargestelltes Detail als Blockschaltbild, und
Fig. 3
einen Achsschnitt eines Senkbremsventils, wie es in den Fig. 1 und 2 verwendet sein kann.
Reference to the drawings, embodiments of the subject invention will be explained. Show it:
Fig. 1
a block diagram of an input section of a hydraulic control device,
Fig. 2
a symbolically represented in Fig. 1 detail as a block diagram, and
Fig. 3
an axial section of a lowering brake valve, as it may be used in Figs. 1 and 2.

Eine hydraulische Steuervorrichtung S in Fig. 1 dient mit einer Druckquelle P und einem Rücklauf R über ein Mehrwege-Steuerventil W zur Richtungs- und Geschwindigkeitssteuerung wenigstens eines Hydroverbrauchers V. Die Druckquelle P ist beispielsweise eine Regelpumpe, mit einem Regelanschluss LS. Alternativ könnte die Druckquelle P eine Konstantpumpe sein, die beispielsweise mit einem Drucklos-Umlaufsystem kombiniert ist, das über den Regelanschluss LS angesteuert wird. Ein Drucklos-Umlaufsystem könnte auch der Regelpumpe 8 zugeordnet sein.A hydraulic control device S in Fig. 1 is used with a pressure source P and a return R via a multi-way control valve W for direction and speed control of at least one hydraulic consumer V. The pressure source P is for example a control pump, with a control connection LS. Alternatively, the pressure source P could be a constant pump, which is combined, for example, with a pressure-free circulating system, which is controlled via the control connection LS. A pressureless circulation system could also be associated with the control pump 8.

In einer Eingangssektion E der hydraulischen Steuervorrichtung S ist ein Not-Aus-Abschaltsystem N enthalten, beispielsweise in einem einzigen Gehäuseblock, an oder in welchem die einzelnen Komponenten zusammengefasst sind.In an input section E of the hydraulic control device S, an emergency stop system N is contained, for example in a single housing block, on or in which the individual components are combined.

Die Druckquelle P ist an eine Druckleitung 1 angeschlossen, die durch ein Trennventil T wahlweise mit einer Versorgungsleitung 2 verbindbar oder von dieser abtrennbar ist.The pressure source P is connected to a pressure line 1, which can be connected by a separating valve T optionally with a supply line 2 or disconnected therefrom.

Die Versorgungsleitung 2 führt zu dem wenigstens einen Mehrwege-Steuerventil W, das an eine Rücklaufleitung 3 zum Rücklauf R angeschlossen ist. In der Eingangssektion E ist ferner eine Rücklaufleitung 4 an den Rücklauf R angeschlossen. Druckbegrenzungsventile 5 zwischen der Druckleitung 1 und der Rücklaufleitung 4 begrenzen den Systemdruck.The supply line 2 leads to the at least one multi-way control valve W, which is connected to a return line 3 to the return R. In the input section E, a return line 4 is also connected to the return R. Pressure limiting valves 5 between the pressure line 1 and the return line 4 limit the system pressure.

An einer Abzweigung 6 der Druckleitung 1 zweigen Steuerleitungen 7, 8 zum Trennventil T (einem 2/2-Wegeventil mit Druckvorsteuerung 9 gegen die Kraft einer Feder 14) ab. Die Steuerleitung 7 führt zur Druckvorsteuerung 9 des Trennventils T, mit der das Trennventil T aus der gezeigten Absperrstellung in die Durchgangsstellung schaltbar ist (Druckleitung 1 mit der Versorgungsleitung 2 verbunden). In der Steuerleitung 8 ist zwischen der Abzweigung 6 und einer Federkammer 10 des Trennventils T ein Not-Aus-Magnetschaltventil M vorgesehen, zweckmäßig ein 2/2-Magnet-Schaltventil, das durch einen Schaltmagneten 12 aus der durch eine Feder 11 eingestellten Durchgangsstellung in eine Absperrstellung verstellbar ist (gegebenenfalls mit Druckvorsteuerung). Von der Federkammer 10 des Trennventils T führt eine Ablassleitung 17 über einen Filter 15 zu einer Blendeneinrichtung B, beispielsweise einem Zweiwege-Stromregler 16, der ausgangsseitig über eine Ablassleitung 17' mit der Rücklaufleitung 4 verbunden ist.At a branch 6 of the pressure line 1 branches control lines 7, 8 to the separating valve T (a 2/2-way valve with pressure pilot 9 against the force of a spring 14). The control line 7 leads to the pressure pilot control 9 of the separating valve T, with which the separating valve T from the shut-off position shown in the passage position can be switched (pressure line 1 connected to the supply line 2). In the control line 8, an emergency stop solenoid valve M is provided between the branch 6 and a spring chamber 10 of the separating valve T, expediently a 2/2-solenoid switching valve by a switching magnet 12 from the set by a spring 11 passage position in a Locking position is adjustable (possibly with pressure pre-control). From the spring chamber 10 of the isolation valve T, a discharge line 17 leads via a filter 15 to a diaphragm device B, for example a two-way flow regulator 16, which is connected on the output side via a discharge line 17 'to the return line 4.

Die Blendeneinrichtung B ist im einfachsten Fall eine Düse. Der Vorzug wird jedoch einem Zweiwege-Stromregler 16 gegeben, der druckunabhängig eine vorbestimmte Druckmittelrate hält.The diaphragm device B is in the simplest case a nozzle. However, the preference is given to a two-way flow regulator 16 which maintains a predetermined pressure medium rate independently of pressure.

Teil der hydraulischen Steuervorrichtung S kann ferner ein Lastdruck-Steuerkreis L sein, der in der Eingangssektion E zu dem Anschluss LS führt, wobei hier eine hydraulische Dämpfvorrichtung D vorgesehen ist, die aus einer Dämpfdrossel 20 und zwei zueinander gegensinnigen Rückschlagventilen 18, 19 sowie einer Drossel 21 besteht.Part of the hydraulic control device S may further be a load pressure control circuit L, which leads in the input section E to the port LS, in which case a hydraulic damping device D is provided, consisting of a Dämpfdrossel 20 and two mutually opposite check valves 18, 19 and a throttle 21 exists.

Ferner kann ein 2/2-Magnet-Schaltventil 23 vorgesehen sein, um den Steuerdruck am Anschluss LS, beispielsweise bei Not-Aus, gewollt zum Rücklauf R zu entlasten.Further, a 2/2-solenoid switching valve 23 may be provided to relieve the control pressure at the port LS, for example, in emergency stop, wanted to return R.

Im Normalbetrieb ist das Not-Aus-Magnet-Schaltventil M bestromt und in der Absperrstellung, so dass die Federkammer 10 des Trennventils T keinen Steuerdruck aus der Steuerleitung 8 erhält. Das Trennventil T wird durch den Steuerdruck in der Steuerleitung 7 an der Vorsteuerseite 9 in die Durchgangsstellung gestellt und in dieser gehalten, so dass die Druckleitung 1 mit der Versorgungsleitung 2 verbunden ist. Die Federkammer 10 ist über die Blendeneinrichtung B zum Rücklauf entlastet. Das 2/2-Magnet-Schaltventil 23 ist ebenfalls bestromt und in der Absperrstellung, so dass am Anschluss LS lastdruckabhängiger Steuerdruck herrscht, mit dem beispielsweise die Fördermenge der Druckquelle P an den Bedarf angepasst wird.In normal operation, the emergency-off solenoid switching valve M is energized and in the shut-off position, so that the spring chamber 10 of the separating valve T receives no control pressure from the control line 8. The isolation valve T is provided by the control pressure in the control line 7 on the pilot side 9 in the passage position and held in this, so that the pressure line 1 is connected to the supply line 2. The spring chamber 10 is relieved via the diaphragm device B to the return. The 2/2-solenoid switching valve 23 is also energized and in the shut-off, so that at the port LS load pressure-dependent control pressure prevails, with the example, the delivery rate of the pressure source P is adapted to the needs.

Bei Not-Aus wird bei gegebenenfalls noch ausgelenktem Mehrwege-Steuerventil W das Not-Aus-Magnet-Schaltventil M entregt, und durch die Feder 11 in die Durchgangsstellung (Fig. 1) verstellt. Die Federkammer 10 erhält über die Steuerleitung 8 Steuerdruck, so dass das Trennventil T durch diesen Steuerdruck und die Kraft der Feder 14 in die Absperrstellung verstellt und in dieser gehalten wird. Die Blendeneinrichtung B, d.h. der Zweiwege-Stromregler 16, lässt nur eine vorbestimmte Druckmittelrate abströmen, beispielsweise zwischen 0,3 und 0,5 l/min, so dass das Trennventil T in der Absperrstellung bleibt und dennoch in der Federkammer 10 zusätzlich zur Kraft der Feder 14 nur ein vorbestimmter Druck herrscht. Gleichzeitig kann, falls vorhanden, das 2/2-Magnet-Schaltventil 23 ebenfalls entregt werden, und die Durchgangsstellung einnehmen, so dass der Steuerdruck am Anschluss LS zum Rücklauf R abgebaut wird.In the event of an emergency stop, the emergency-off solenoid switching valve M is de-energized if the multi-way control valve W is still deflected, and is displaced by the spring 11 into the passage position (FIG. 1). The spring chamber 10 receives via the control line 8 control pressure, so that the separating valve T is adjusted by this control pressure and the force of the spring 14 in the shut-off position and held in this. The diaphragm device B, i. the two-way flow regulator 16, allows only a predetermined pressure medium rate to flow, for example between 0.3 and 0.5 l / min, so that the separating valve T remains in the shut-off position and yet in the spring chamber 10 in addition to the force of the spring 14 only a predetermined Pressure prevails. At the same time, if present, the 2/2-solenoid switching valve 23 can also be de-energized, and take the passage position, so that the control pressure at the port LS to return R is reduced.

Ist später wieder auf Normalbetrieb umzuschalten, dann werden das Not-Aus-Magnet-Schaltventil M und das, falls vorhanden, 2/2-Magnet-Schaltventil 23 bestromt und in ihre Absperrstellungen verstellt, so dass das Trennventil T die Druckleitung 1 wieder mit der Versorgungsleitung 2 verbindet und am Anschluss LS Steuerdruck aufgebaut wird.Is later switch back to normal operation, then the emergency stop solenoid switching valve M and, if present, 2/2-solenoid switching valve 23 energized and adjusted in their shut-off, so that the isolation valve T, the pressure line 1 again with the Supply line 2 connects and at connection LS control pressure is built up.

Fig. 2 verdeutlicht als Blockschaltbild die Ausgestaltung des Zweiwege-Stromreglers 16 von Fig. 1, der zwischen der Federkammer 10 und dem Rücklauf R angeordnet ist. Der Zweiwege-Stromregler 16 weist in der Ablaufleitung 17 eine kleinere Zulaufblende 24 auf. Stromauf der Zulaufblende 24 zweigt eine Steuerleitung 25 zur Schließseite eines 2/2-Regelventils 27 ab. Stromab der Zulaufblende 24 zweigt eine weitere Steuerleitung 26 zur Aufsteuerseite des 2/2-Regelventils ab, an der auch eine Regelfeder 33 wirkt. Im 2/2-Regelventil 27 ist eine gegenüber der Zulaufblende 24 größere Ablaufblende 36 vorgesehen, deren Abströmquerschnitt nach Maßgabe der Drücke in den Steuerleitung 25, 26 (nach Art einer Druckwaage) ausgehend von einer Maximalgröße verkleinert wird, derart, dass die in die Ablaufleitung 17' abströmende Druckmittelrate konstant bleibt. Dieser Zweiwege-Stromregler 16 kann durch verschiedene Hydraulikkomponenten gebildet werden, oder ist zweckmäßig ein handelsübliches Senkbremsventil SB gemäß Fig. 3, das hier als Einschraub-Senkbremsventil ausgebildet ist.Fig. 2 illustrates a block diagram of the embodiment of the two-way flow regulator 16 of FIG. 1, which is arranged between the spring chamber 10 and the return R. The two-way flow regulator 16 has a smaller inlet aperture 24 in the drain line 17. Upstream of the inlet panel 24, a control line 25 branches to the closing side of a 2/2 control valve 27 from. Downstream of the inlet orifice 24, a further control line 26 branches off to the control side of the 2/2 control valve, at which a control spring 33 also acts. In the 2/2 control valve 27, a larger than the inlet aperture 24 drain aperture 36 is provided, the outflow cross section is reduced in accordance with the pressures in the control line 25, 26 (in the manner of a pressure balance) starting from a maximum size, such that in the drain line 17 'outflowing pressure medium rate remains constant. This two-way flow regulator 16 can be formed by various hydraulic components, or is expediently a commercial Senkbremsventil SB of FIG. 3, which is designed here as a screw-Senkbremsventil.

Das Senkbremsventil SB hat ein äußeres Einschraubgehäuse 28 mit einer Drehhandhabe 29, einem Außengewinde 30 und einer Umfangsdichtung 31. Im Außengehäuse 28 ist dort, wo die Ablaufleitung 17 angeschlossen wird, eine stationäre Steuerkante 37 geformt. Im Außengehäuse 28 ist ein Blendenkolben 32 verschiebbar geführt, der durch die Regelfeder 33 in Richtung zu einem Anschlag 39 belastet wird. Die Regelfeder 33 stützt sich im Außengehäuse 28 auf einem Federwiderlager 38 ab. Die Ablaufleitung 17 aus der Federkammer 10 mündet im oberen offenen Ende des Außengehäuses 28, d.h. dort, wo der Blendenkolben 32 wenigstens die kleinere Zulaufblende 24 aufweist. Ferner ist im Blendenkolben 32 wenigstens eine Ablaufblende 36 geformt, die mit der Steuerkante 37 kooperiert. Je höher der Zulaufdruck (das Druckgefälle über die Zulaufblende 24) ist, desto weiter wird der Blendenkolben 32 gegen die Regelfeder 33 verschoben, und desto kleiner wird der Abflussquerschnitt aus der Ablaufblende 36, die zunehmend von der Steuerkante 37 abgedrosselt wird.The lowering brake valve SB has an outer screw-in housing 28 with a rotary handle 29, an external thread 30 and a peripheral seal 31. In the outer housing 28, where the drain line 17 is connected, a stationary control edge 37 is formed. In the outer housing 28, a diaphragm piston 32 is slidably guided, which is loaded by the control spring 33 in the direction of a stop 39. The control spring 33 is supported in the outer housing 28 on a spring abutment 38. The drain line 17 from the spring chamber 10 opens in the upper open end of the outer housing 28, i. where the orifice piston 32 has at least the smaller inlet orifice 24. Further, in the orifice piston 32 at least one drain aperture 36 is formed, which cooperates with the control edge 37. The higher the inlet pressure (the pressure gradient across the inflow orifice 24), the further the orifice piston 32 is displaced against the control spring 33, and the smaller the outflow cross-section of the drainage orifice 36, which is increasingly throttled by the control edge 37.

Claims (9)

Hydraulische Steuervorrichtung (S) für wenigstens einen Hydroverbraucher (V), dessen wenigstens eine Arbeitsleitung über ein Wegesteuerventil (W) mit einer Druckquelle (P) und einem Rücklauf (R) verbindbar ist, mit einem Lastdruck-Steuerkreis (L), und mit einem Not-Aus-Abschaltsystem (N), das ein Magnetschaltventil (M) und ein zumindest zu einer Durchgangsstellung druckvorgesteuertes, zur Sperrstellung federbeaufschlagtes Trennventil (T) zwischen der Druckquelle (P) und einer zum Wegesteuerventil (W) führenden Versorgungsleitung (2) sowie ein zwischen der Druckquelle (P) und dem Trennventil (T) vorgesehenes Magnetschaltventil (M) aufweist, wobei eine Federkammer (10) des Trennventils (T) an den Rücklauf (R) angeschlossen ist, dadurch gekennzeichnet, dass das Magnetschaltventil (M) ein 2/2-Wegeventil und zwischen der Druckquelle (P) und der Federkammer (10) des Trennventils (T) angeordnet ist, dass das Trennventil (T) ein 2/2-Wegeventil ist, dessen für die Einstellung der Durchgangsstellung vorgesehene Druckvorsteuerseite (9) permanent mit der Druckquelle (P) verbunden ist, und dass zwischen der Federkammer (10) und dem Rücklauf (R) wenigstens eine Blendeneinrichtung (B) vorgesehen ist.Hydraulic control device (S) for at least one hydraulic consumer (V), whose at least one working line via a directional control valve (W) with a pressure source (P) and a return (R) is connectable, with a load pressure control circuit (L), and with a Emergency-stop system (N), the one solenoid switching valve (M) and at least one passage position druckvorgesteuertes, to the blocking position spring-loaded isolation valve (T) between the pressure source (P) and a directional control valve (W) leading supply line (2) and a between the pressure source (P) and the separating valve (T) provided magnetic switching valve (M), wherein a spring chamber (10) of the separating valve (T) to the return line (R) is connected, characterized in that the magnetic switching valve (M) a 2 / 2-way valve and between the pressure source (P) and the spring chamber (10) of the separating valve (T) is arranged, that the separating valve (T) is a 2/2-way valve, for the adjustment of Durchgan gsstellung provided pressure pilot side (9) is permanently connected to the pressure source (P), and that between the spring chamber (10) and the return (R) at least one aperture device (B) is provided. Hydraulische Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass zwischen der Federkammer (10) und dem Rücklauf (R) als die Blendeneinrichtung (B) ein Zweiwege-Stromregler (16) angeordnet ist, mit dem druckunabhängig eine vorbestimmte Druckmittelrate einstellbar ist.Hydraulic control device according to claim 1, characterized in that between the spring chamber (10) and the return (R) as the diaphragm device (B) a two-way flow regulator (16) is arranged, with the pressure-independent, a predetermined pressure medium rate is adjustable. Hydraulische Steuervorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass die Druckmittelrate auf ca. 0,3 bis 0,5 l/min eingestellt ist.Hydraulic control device according to claim 2, characterized in that the pressure medium rate is set to about 0.3 to 0.5 l / min. Hydraulische Steuervorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass der Zweiwege-Stromregler (16) ein handelsübliches Senkbremsventil (SB), vorzugsweise ein Einschraubsenkbremsventil, ist.Hydraulic control device according to claim 2, characterized in that the two-way flow regulator (16) is a commercially available lowering brake valve (SB), preferably a Einschraubsenkbremsventil. Hydraulische Steuervorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass das Senkbremsventil (SB) einen zulaufseitig gegen die Kraft einer Feder (33) verschiebbaren Blendenkolben (32) mit wenigstens einer kleineren Zulaufblende (24) und wenigstens einer größeren Ablaufblende (36) enthält, und dass mit der Ablaufblende (36) eine stationäre Steuerkante (37) derart zusammenwirkt, dass der Abströmquerschnitt aus der Ablaufblende (36) mit steigendem Zulaufdruck verringert wird.Hydraulic control device according to claim 4, characterized in that the lowering brake valve (SB) a supply side against the force of a spring (33) displaceable Aperture piston (32) with at least one smaller inlet orifice (24) and at least one larger drain orifice (36), and in that with the drainage orifice (36) a stationary control edge (37) cooperates such that the outflow cross-section from the drainage orifice (36) with increasing Inlet pressure is reduced. Hydraulische Steuervorrichtung nach wenigstens einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Druckquelle (P) eine aus dem Lastdruck-Steuerkreis (L) geregelte Regelpumpe ist.Hydraulic control device according to at least one of claims 1 to 5, characterized in that the pressure source (P) is a regulated from the load pressure control circuit (L) control pump. Hydraulische Steuervorrichtung nach wenigstens einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Druckquelle (P) eine Konstantpumpe ist.Hydraulic control device according to at least one of claims 1 to 5, characterized in that the pressure source (P) is a fixed displacement pump. Hydraulische Steuervorrichtung nach wenigstens einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass zwischen dem Lastdrucksteuerkreis (L) und der Druckquelle (P) eine hydraulische Dämpfvorrichtung (D) vorgesehen ist, die eine Dämpfdrossel (20) und zwei die Dämpfdrossel (20) umgehende, zueinander gegensinnig angeordnete Rückschlagventile (18, 19) enthält.Hydraulic control device according to at least one of claims 1 to 7, characterized in that between the load pressure control circuit (L) and the pressure source (P), a hydraulic damping device (D) is provided which bypasses a Dämpfdrossel (20) and two the damping throttle (20) , Check valves (18, 19) arranged opposite to each other contains. Hydraulische Steuervorrichtung nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Not-Aus-Magnetschaltventil (M), das Trennventil (T) und die Blendenanordnung (B) in einem Eingangssektions-Gehäuseblock (E) der, vorzugsweise von einer Regelpumpe (P) versorgten, hydraulischen Steuervorrichtung angeordnet sind.Hydraulic control device according to at least one of the preceding claims, characterized in that the emergency stop solenoid valve (M), the isolation valve (T) and the diaphragm assembly (B) in an input section housing block (E), preferably by a control pump (P ), hydraulic control device are arranged.
EP20050019936 2005-01-28 2005-09-13 Hydraulic control device Expired - Fee Related EP1686268B1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10962031B2 (en) 2016-04-01 2021-03-30 Hydac Systems & Services Gmbh Control device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3258116B1 (en) * 2016-06-15 2019-12-25 HAWE Hydraulik SE Hydraulic module with pressure-controlled 2-way flow control valve

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4324177A1 (en) 1992-08-10 1994-02-17 Heilmeier & Weinlein Hydraulic controller, for use in e.g. cranes - contains emergency-stop valve pre-controlling pressure to isolating valve of pressure regulating pump.
DE19904616A1 (en) 1999-02-05 2000-08-10 Mannesmann Rexroth Ag Control arrangement for at least two hydraulic consumers and pressure differential valve therefor

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE510508C2 (en) * 1993-06-11 1999-05-31 Voac Hydraulics Boraas Ab Device for controlling a hydraulic motor

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4324177A1 (en) 1992-08-10 1994-02-17 Heilmeier & Weinlein Hydraulic controller, for use in e.g. cranes - contains emergency-stop valve pre-controlling pressure to isolating valve of pressure regulating pump.
DE19904616A1 (en) 1999-02-05 2000-08-10 Mannesmann Rexroth Ag Control arrangement for at least two hydraulic consumers and pressure differential valve therefor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10962031B2 (en) 2016-04-01 2021-03-30 Hydac Systems & Services Gmbh Control device

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EP1686268B1 (en) 2011-12-28
DE202005001417U1 (en) 2006-06-08
EP1686268A3 (en) 2009-05-20
ES2377386T3 (en) 2012-03-27

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