EP3436705B1 - Control device - Google Patents

Control device Download PDF

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Publication number
EP3436705B1
EP3436705B1 EP17711095.4A EP17711095A EP3436705B1 EP 3436705 B1 EP3436705 B1 EP 3436705B1 EP 17711095 A EP17711095 A EP 17711095A EP 3436705 B1 EP3436705 B1 EP 3436705B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
hydraulic
pilot
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.)
Active
Application number
EP17711095.4A
Other languages
German (de)
French (fr)
Other versions
EP3436705A1 (en
Inventor
Christoph Stönner
Sascha Alexander Biwersi
Peter Jakobs
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.)
Hydac Systems and Services GmbH
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Hydac Systems and Services GmbH
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Publication date
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Publication of EP3436705A1 publication Critical patent/EP3436705A1/en
Application granted granted Critical
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    • 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
    • F15B11/166—Controlling a pilot pressure in response to the load, i.e. supply to at least one user is regulated by adjusting either the system pilot pressure or one or more of the individual pilot command pressures
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B66C13/20—Control systems or devices for non-electric drives
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/88—Safety gear
    • B66C23/90—Devices for indicating or limiting lifting moment
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0807—Manifolds
    • F15B13/0817—Multiblock manifolds
    • 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
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/329—Directional 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • 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
    • F15B2211/60—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
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or filtering
    • 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • 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
    • F15B2211/85—Control during special operating conditions
    • 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
    • F15B2211/86—Control during or prevention of abnormal conditions
    • 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 control device with the features of the preamble of patent claim 1.
  • a hydraulic control device for at least one hydraulic consumer is known, the at least one working line of which can be connected to a pressure source and a return via a directional control valve, to a load pressure control circuit and to an emergency stop switch-off system which is connected between the pressure source and a supply line leading to the directional control valve has a pressure-controlled at least to a through position, spring-loaded isolation valve to the blocking position and a magnetic switching valve provided between the pressure source and the isolation valve, wherein a spring chamber of the isolation valve is connected to the return, the magnetic switching valve being a 2/2-way valve which is located between the pressure source and the spring chamber of the isolating valve is arranged, the isolating valve being a 2/2-way valve, the pressure pilot side of which is provided for the setting of the passage position is permanently connected to the pressure source, and wherein between the spring chamber u nd the return is provided at least one aperture device.
  • the two 2/2-way valves are, on the one hand, a solenoid valve and, on the other hand, a pressure pilot operated against spring force Valve.
  • the isolating valve is not held in the open position via the emergency stop solenoid switching valve, but rather via the pilot pressure derived from the delivery pressure of the pressure source.
  • the emergency stop solenoid valve is de-energized and switched to its open position so that the control pressure then acting parallel to the spring adjusts and maintains the shut-off position of the isolating valve.
  • the above-mentioned orifice device between the spring chamber and the return enables a permanent outflow of pressure medium without endangering the shut-off position of the isolating valve.
  • the pilot pressure generation is arranged in a connection plate parallel to the emergency shutdown system. This means that with constant pump systems as well as variable pump systems, sufficient pressure can always be generated in the pilot control circuit without further secondary measures. Regardless of the mentioned emergency stop function, it is thus possible to deflect the control spool of the working sections in the case of an electro-hydraulic control with internal pilot pressure generation. In this case, the hydraulic energy flow from the pump with the pressure supply connection P to the respective work connection A or B and thus to the connected hydraulic consumer can be prevented by the emergency stop function; but not the energy flow from work port A or B to the tank or return T.
  • DE 197 14 141 A1 discloses a generic control device for at least one hydraulic working section, which has a hydraulic supply circuit and a pilot pressure-supplied control valve Pressure supply source and a return line can be connected, with a control block which has at least one useful connection for the respective hydraulic working section, a pressure supply source connection and a return connection, and with an emergency stop switch-off device which has a pilot solenoid valve and a further valve has, by means of the pilot solenoid valve both the hydraulic energy flow from the pressure supply source to at least one of the respective working sections and the pilot pressure supply to the control valve via the further valve can be prevented.
  • the object of the invention is therefore to further improve a control device of the type mentioned in such a way that increased safety in operation is achieved.
  • a related object is achieved by a control device with the features of claim 1 in its entirety.
  • a control device is characterized in accordance with the characterizing part of patent claim 1 in that the emergency stop switch-off device, in addition to the pilot solenoid valve, has a switch valve as a further valve which, in the manner of an OR element, depends on the actuation state of the pilot valve. Solenoid valve which optionally enables fluid supply when the emergency stop function is not actuated at least one hydraulic working section via the respective useful connection and when the emergency stop function is actuated at least one additional hydraulic working section via the respective useful connection.
  • a switch valve according to the invention preferably in the form of a 3/2-way valve, as a further valve of the emergency stop switch-off device instead of a "unidirectional" 2/2-way valve
  • the switching logic can then be expanded in such a way that the system can also be used as a kind of OR element or OR function in the overall hydraulic system of mobile work machines in order to implement a turnout that can be used then go to different work sections.
  • both the hydraulic energy flow from the pressure supply source to at least one of the respective working sections and the pilot pressure supply to the control valve via the additional valve can be prevented by means of the pilot solenoid valve, this is also achieved in the case of pressing or pulling loads on the working connections of the control blocks that when the emergency stop function is actuated, there can still be no unwanted movements on the consumers.
  • connection "A1" version of the control device two different hydraulic circuits can be optionally supplied via the OR link and can be operated completely decoupled from a safety point of view.
  • This version can be used to control a hydraulic work section with a hydraulic consumer, for example in the form of a crane or lifting arm with a hydraulically actuated working cylinder, which can be switched off or disconnected from the pressure supply via an upstream pilot pressure-supplied control valve, provided the emergency stop Valve (pilot solenoid valve) actuates a corresponding switch position at the switch valve (3/2-way valve), which then directly produces the hydraulic supply for another hydraulic working section, for example can consist of hydraulically actuated support cylinders of a mobile crane or the like, which then ensure that the mobile crane cannot fall over under any circumstances even under load of the control device.
  • a hydraulic consumer for example in the form of a crane or lifting arm with a hydraulically actuated working cylinder, which can be switched off or disconnected from the pressure supply via an upstream pilot pressure-supplied control valve, provided the emergency stop Val
  • connection "T1" instead of connection "A1", in particular constant pump systems can then be switched between the internal working group of the respective working sections and the neutral circulation in the direction of the tank or return flow T via the connection "T1".
  • the generally common neutral circulation is preferably carried out via a circulation pressure compensator in the connection plate of the device, and since this is always spring-loaded depending on the valve construction and design, this spring preload is generally between 9 and 16 bar depending on the spring preload Combination with the pump volume flow as power loss. Since the switch valve or the OR element does not perform any control tasks, but should only be designed as a switching valve, the spring force mentioned can accordingly be dimensioned lower. Using this logic, the loss line can be reduced by a factor of 3 to 4 compared to conventional systems as described and combined with the safety shutdown.
  • a further current regulator is preferably provided on the pressure supply side to the pilot valves of the control valve, which contributes to the fact that small leaks are discharged via the emergency stop valve in the direction of the control oil tank line Z of the pilot pressure control for the control valve and thus the pressure signal at the measurement connection MS is not adulterated.
  • control device solution according to the invention are the subject of the dependent claims.
  • connection point P of a conventional pressure supply source can in turn be supplied in the usual manner with fluid that can be predetermined by a constant or variable displacement pump (not shown).
  • a pump line 10 ends on the input side of a circulation pressure compensator 12, a switch valve 14 and a pilot solenoid valve 16.
  • these open into a return line or tank line, which leads to the return or tank connection T.
  • the outlet side of the valve 14 also opens into the return line or tank line.
  • the circulation pressure compensator 12 is connected with its two opposite control sides to control lines which are supplied via the pump line 10, with a view towards the Fig. 1 seen the upper control line is connected to the pump line 10 via an orifice or throttle 20.
  • the circulation pressure compensator 12 is spring-supported in its in the Fig. 1 shown closed or locked position held in the uncontrolled state. If rectangular diagrams are shown in the circuit diagram that are penetrated by a fluid line or fluid passage point, they are so-called empty or placeholders that can be equipped with further hydraulic components if necessary.
  • the switch valve 14 is present, which is designed as a 3/2-way switching valve and from the understanding of the switching logic forms a kind of "OR element".
  • the switch valve 14 establishes a fluid-carrying connection between the pump line 10 and the connection A1.
  • the two opposite control lines for the switch valve 14 are in turn connected to the pump line 10, looking in the direction of the Fig. 1 seen in the lower control line, an aperture or throttle 22 is connected.
  • the pilot solenoid valve 16 is provided, which is shown spring-loaded in its shown blocking position or "normally closed” position. If the valve 16 is switched solenoid operated, it reaches its open position and establishes a fluid connection between the pump line 10 and the return line or tank line 18.
  • a protective filter 24 and a current regulator 26 are connected between the two input sides of the valves 14, 16. Between the protective filter 24 and the current regulator 26, a connection point MP opens out of the control block 30 of the control device, shown in broken lines, as seen from the pump line 10.
  • a block 32 is again shown in broken lines, which comprises the essential components of the emergency stop switch-off device, consisting in particular of the switch valve 14, the pilot solenoid valve 16 and the protective filter 24 and the current regulator 26.
  • a conventional pilot pressure-supplied control valve 34 which is shown in FIG Fig. 1 is shown in its blocked valve slide position with an input-side connection point which is connected to the load-sensing line LS via a shuttle valve 36.
  • the valve spool of the control valve 34 reaches in its direction of view Fig. 1 seen lower switching position, the supply or pump pressure in the pump line 10 is passed on via the supply line 38 connected to the output side to the switch valve 14 and the control valve 34 on the output side of the control valve 34 to the useful port A, whereas the useful port B via the control valve 34 is connected to the return or tank connection T in this switching position. If the control slide of the valve 34 in its Fig.
  • the service port B is supplied with the pump pressure and the service port A is switched to return or tank T.
  • the spring-loaded control valve spool of the valve 34 serve two pilot valves 40, each of which has its own control via the control lines Z, C, of which, however, for the sake of simplicity, the fluid flow is only shown for one pilot valve 40, in that the control line Z leads to the one pilot valve and the further control line C. to the other pilot valve 40.
  • a connection line 42 also opens into the control oil tank line of the control line Z for the respective pilot valve 40, into which a further current regulator 44 in the form of a valve is preferably connected, the connection line 42 being connected to the supply line 38 at a branch point 46.
  • the control line Z is permanently connected to the pressure-supplying pump line 10 via a pressure limiting valve 48 and via the orifice or throttle 20.
  • a filter device 50 together with a further pressure control valve 52 is used for internal pilot pressure generation for the pilot valves 40 as part of the electro-hydraulic slide valve actuation for the individual working sections.
  • the further pressure control valve 52 is connected on the output side to the further control line C.
  • the control lines Z, C are shown at the output of the control block 30 opening into corresponding connection points Z, C.
  • the load-sensing line LS is shown on the output side at block 30 opening into the connection point LS.
  • the supply line 38 On the input side of the control valve 34, the supply line 38 is shown opening into a flow control valve 54 which is controlled by a load-sensing pressure of the control valve 34, as shown. Furthermore, the supply line 38 opens out in the direction of viewing Fig. 1 seen at its lower end in a measuring connection MS, to which a PI pressure sensor 56 can be connected.
  • connection points A, B with the formation of a first hydraulic working section a hydraulic working cylinder, not shown, can be connected with its two fluid or working spaces, the working cylinder being intended to control the crane or lifting arm of a mobile crane.
  • a further hydraulic working section is connected to the connection point A1, which in turn supplies hydraulic support cylinders which, when extended, stabilize the platform of the mobile crane so that it cannot fall over or buckle on one side during operation.
  • the use of the control device mentioned is only exemplary; other possible uses are conceivable.
  • the switch valve 14 switches to its lower switching position and then supplies the respective pilot valve 40 with pump pressure via the pump line 10, as already described, which leads to a corresponding deflection of the control slide of the Control valve 34 leads and the connection points A or B of the first hydraulic working section are supplied with fluid pressure that can be predetermined to actuate the same. If the pilot valve 16 is not actuated and reaches its normally closed position shown, the switch valve 14 is spring actuated into its in Fig. 1 brought position shown and then follows only a fluid supply under pressure via the pump line 10 in the direction of the connection point A1 with the further hydraulic working section.
  • the support cylinders for the platform of the mobile crane are then supplied accordingly, which serves for safety, since they can then perform their support function.
  • the supply line 38 is then shut off from the pressure supply, which means that the respective pilot valve 40 is no longer actuated and the valve slide of the control valve 34 thus reaches its blocking basic position with spring support, as shown after Fig. 1 and thus surely prevents the fluid supply for the first hydraulic working section with the supply via the respective service connections A or B.
  • the supply is reliably prevented in the first working section, even with pulling or pushing loads, in such a way that the hydraulic consumer connected in the first working section can no longer move.
  • the hydraulic energy flow from the pressure supply to the respective first working section as well as the pilot pressure supply of the electro-hydraulic control slide control for the control valve 34 can be interrupted at the same time, which has no correspondence in the prior art.
  • pilot solenoid valve 16 instead of the solenoid valve 16 as shown in the Fig. 1 which is normally closed, another pilot solenoid valve can optionally be used if necessary, which is normally open in the basic position (normally open) and actuated to its closed blocking position. Depending on the type of pilot valve 16 then used, it can then be decided which position the emergency stop valve 14 should be deenergized or energized and which circuit is activated with the hydraulic working sections (A, B, A1). Due to the arrangement with the protective filter 24 and the hydraulically connected current regulator 26 as an orifice device, the respective pilot solenoid valve 16 can be reliably protected from dirt, which helps to significantly reduce the possible failure risk of the required safety function.
  • the Fig. 2 shows the conditions of the control block 30 in the direction of view to the left of the control valve 34 for improved illustration. The statements made so far also apply to the hydraulic components according to the Fig. 2 .
  • the Fig. 3 again corresponds to the representation according to Fig. 2 with the proviso that the PI pressure sensor 56 is not shown on the measurement connection MS and instead of the connection A1 for a further hydraulic working section, the corresponding connection point with the designation T1 has been modified, which opens up the possibility, especially for the use of constant pump systems either between the internal working group of the respective working section and the neutral circulation in the direction of the return or tank connection T via the connection T1 as shown in the figure Fig. 3 to choose.
  • the usual neutral circulation in the above-mentioned constant pump systems takes place via the circulation pressure compensator 12 already described, which, as shown, is always spring-loaded on one side and, depending on the spring preload, generally between 9 and 16 bar, results in a power loss in combination with the pump volume flow .
  • the switch valve 14 in the form of the OR element does not have to perform any control tasks, but only has to be designed as a simple switching valve, the spring force for the circulating pressure compensator 12 can accordingly be dimensioned lower. In this way, the power loss can be reduced by a factor of 3 to 4 compared to conventional systems and combined with the safety circuit.

Description

Die Erfindung betrifft eine Steuervorrichtung mit den Merkmalen des Oberbegriffs von Patentanspruch 1.The invention relates to a control device with the features of the preamble of patent claim 1.

Durch die EP 1 686 268 B1 ist eine hydraulische Steuervorrichtung für wenigstens einen Hydroverbraucher bekannt, dessen wenigstens eine Arbeitsleitung über ein Wegesteuerventil mit einer Druckquelle und einem Rücklauf verbindbar ist, mit einem Lastdruck-Steuerkreis und mit einem Not-Aus-Abschaltsystem, das zwischen der Druckquelle und einer zum Wegesteuerventil führenden Versorgungsleitung ein zumindest zu einer Durchgangsstellung druckvorgesteuertes, zur Sperrstellung federbeaufschlagtes Trennventil sowie ein zwischen der Druckquelle und dem Trennventil vorgesehenes Magnetschaltventil aufweist, wobei eine Federkammer des Trennventils an den Rücklauf angeschlossen ist, wobei das Magnetschaltventil ein 2/2-Wegeventil ist, welches zwischen der Druckquelle und der Federkammer des Trennventils angeordnet ist, wobei das Trennventil ein 2/2-Wegeventil ist, dessen für die Einstellung der Durchgangsstellung vorgesehene Druckvorsteuerseite permanent mit der Druckquelle verbunden ist, und wobei zwischen der Federkammer und dem Rücklauf wenigstens eine Blendeneinrichtung vorgesehen ist.Through the EP 1 686 268 B1 A hydraulic control device for at least one hydraulic consumer is known, the at least one working line of which can be connected to a pressure source and a return via a directional control valve, to a load pressure control circuit and to an emergency stop switch-off system which is connected between the pressure source and a supply line leading to the directional control valve has a pressure-controlled at least to a through position, spring-loaded isolation valve to the blocking position and a magnetic switching valve provided between the pressure source and the isolation valve, wherein a spring chamber of the isolation valve is connected to the return, the magnetic switching valve being a 2/2-way valve which is located between the pressure source and the spring chamber of the isolating valve is arranged, the isolating valve being a 2/2-way valve, the pressure pilot side of which is provided for the setting of the passage position is permanently connected to the pressure source, and wherein between the spring chamber u nd the return is provided at least one aperture device.

Bei der bekannten Lösung sind die beiden 2/2-Wegeventile zum einen ein Magnetventil sowie zum anderen ein gegen Federkraft druckvorgesteuertes Ventil. Im Normalbetrieb wird bei der bekannten Lösung das Trennventil nicht über das Not-Aus-Magnetschaltventil in der Durchgangsstellung gehalten, sondern über den vom Förderdruck der Druckquelle abgeleiteten Vorsteuerdruck. Bei Not-Aus wird das Not-Aus-Magnetschaltventil entregt und in seine Durchgangsstellung geschaltet, so dass der dann parallel zur Feder wirkende Steuerdruck die Absperrstellung des Trennventils einstellt und hält. Die genannte Blendeneinrichtung zwischen der Federkammer und dem Rücklauf ermöglicht einen permanenten Abfluss von Druckmittel, ohne die Absperrstellung des Trennventils zu gefährden.In the known solution, the two 2/2-way valves are, on the one hand, a solenoid valve and, on the other hand, a pressure pilot operated against spring force Valve. In normal operation, in the known solution, the isolating valve is not held in the open position via the emergency stop solenoid switching valve, but rather via the pilot pressure derived from the delivery pressure of the pressure source. In the event of an emergency stop, the emergency stop solenoid valve is de-energized and switched to its open position so that the control pressure then acting parallel to the spring adjusts and maintains the shut-off position of the isolating valve. The above-mentioned orifice device between the spring chamber and the return enables a permanent outflow of pressure medium without endangering the shut-off position of the isolating valve.

Bei der bekannten Lösung ist die Vorsteuerdruckerzeugung in eine Anschlussplatte parallel zum Not-Aus-Abschaltsystem angeordnet. Das bedeutet, dass sowohl bei Konstant-Pumpensystemen als auch Verstellpumpen-Systemen ohne weitere Sekundärmaßnahmen immer genügend Druck im Vorsteuerkreis erzeugt werden kann. Unabhängig von der angesprochenen Not-Aus-Funktion ist es somit möglich, die Steuerschieber der Arbeitssektionen bei einer elektrohydraulischen Ansteuerung mit interner Pilotdruckerzeugung auszulenken. Dabei kann zwar durch die Not-Aus-Funktion der hydraulische Energiefluss von der Pumpe mit dem Druckversorgungsanschluss P zum jeweiligen Arbeitsanschluss A oder B und somit zum angeschlossenen hydraulischen Verbraucher verhindert werden; nicht aber der Energiefluss vom Arbeitsanschluss A oder B zum Tank oder Rücklauf T. Da in der Praxis nicht selten drückende oder ziehende Lasten an den Arbeitsanschlüssen der Steuerblöcke mobiler Arbeitsmaschinen vorliegen und sich somit auf dem Steuerschieber abstützen, kann es trotz der Not-Aus-Funktion im Pumpenzulauf zu ungewollten Bewegungen an den Verbrauchern kommen, was ein Sicherheitsrisiko darstellt.In the known solution, the pilot pressure generation is arranged in a connection plate parallel to the emergency shutdown system. This means that with constant pump systems as well as variable pump systems, sufficient pressure can always be generated in the pilot control circuit without further secondary measures. Regardless of the mentioned emergency stop function, it is thus possible to deflect the control spool of the working sections in the case of an electro-hydraulic control with internal pilot pressure generation. In this case, the hydraulic energy flow from the pump with the pressure supply connection P to the respective work connection A or B and thus to the connected hydraulic consumer can be prevented by the emergency stop function; but not the energy flow from work port A or B to the tank or return T. Since in practice it is not uncommon for pushing or pulling loads to be present on the work ports of the control blocks of mobile machines and thus to be supported on the control spool, it can be used despite the emergency stop function undesired movements of the consumers occur in the pump inlet, which represents a safety risk.

DE 197 14 141 A1 offenbart eine gattungsgemäße Steuervorrichtung für mindestens eine hydraulische Arbeitssektion, die über einen hydraulischen Versorgungskreis und ein pilotdruckversorgtes Steuerventil mit einer Druckversorgungsquelle und einem Rücklauf verbindbar ist, mit einem Steuerblock, der mindestens einen Nutzanschluss für die jeweilige hydraulische Arbeitssektion, einen Druckversorgungsquellen-Anschluss und einen Rücklauf-Anschluss aufweist, und mit einer Not-Aus-Abschalteinrichtung, die ein Vorsteuer-Magnetventil sowie ein weiteres Ventil aufweist, wobei mittels des Vorsteuer-Magnetventils sowohl der hydraulische Energiefluss von der Druckversorgungsquelle zu mindestens einer der jeweiligen Arbeitssektionen als auch die Pilotdruckversorgung zu dem Steuerventil über das weitere Ventil unterbindbar ist. DE 197 14 141 A1 discloses a generic control device for at least one hydraulic working section, which has a hydraulic supply circuit and a pilot pressure-supplied control valve Pressure supply source and a return line can be connected, with a control block which has at least one useful connection for the respective hydraulic working section, a pressure supply source connection and a return connection, and with an emergency stop switch-off device which has a pilot solenoid valve and a further valve has, by means of the pilot solenoid valve both the hydraulic energy flow from the pressure supply source to at least one of the respective working sections and the pilot pressure supply to the control valve via the further valve can be prevented.

Weitere Steuervorrichtungen für hydraulische und hydrostatische Systeme sind aus EP 1 686 268 B1 und DE 103 42 789 A1 bekannt.Other control devices for hydraulic and hydrostatic systems are off EP 1 686 268 B1 and DE 103 42 789 A1 known.

Ausgehend von diesem Stand der Technik liegt daher der Erfindung die Aufgabe zugrunde, eine Steuervorrichtung der genannten Art dahingehend weiter zu verbessern, dass eine erhöhte Sicherheit im Betrieb erreicht ist. Eine dahingehende Aufgabe löst eine Steuervorrichtung mit den Merkmalen des Patentanspruchs 1 in seiner Gesamtheit.Starting from this prior art, the object of the invention is therefore to further improve a control device of the type mentioned in such a way that increased safety in operation is achieved. A related object is achieved by a control device with the features of claim 1 in its entirety.

Eine erfindungsgemäße Steuervorrichtung zeichnet sich gemäß dem kennzeichnenden Teil des Patentanspruchs 1 dadurch aus, dass die Not-Aus-Abschalteinrichtung neben dem Vorsteuer-Magnetventil als weiteres Ventil über ein Weichenventil verfügt, das in der Art eines Oder-Gliedes in Abhängigkeit des Betätigungszustands des Vorsteuer-Magnetventils die wahlweise Fluidversorgung bei nicht-betätigter Not-Aus-Funktion mindestens der einen hydraulischen Arbeitssektion über den jeweiligen Nutzanschluss und bei betätigter Not-Aus-Funktion mindestens einer weiteren hydraulischen Arbeitssektion über den jeweiligen Nutzanschluss ermöglicht.A control device according to the invention is characterized in accordance with the characterizing part of patent claim 1 in that the emergency stop switch-off device, in addition to the pilot solenoid valve, has a switch valve as a further valve which, in the manner of an OR element, depends on the actuation state of the pilot valve. Solenoid valve which optionally enables fluid supply when the emergency stop function is not actuated at least one hydraulic working section via the respective useful connection and when the emergency stop function is actuated at least one additional hydraulic working section via the respective useful connection.

Durch den erfindungsgemäßen Einsatz eines Weichenventils, vorzugsweise in Form eines 3/2-Wegeventils, als weiteres Ventil der Not-Aus-Abschalteinrichtung anstelle eines "unidirektional" wirkenden 2/2-Wegeventils nach der vorstehend beschriebenen bekannten Lösung kann die Schaltlogik dann dahingehend erweitert werden, dass man das System gleichzeitig auch als eine Art Oder-Glied oder Oder-Funktion im Gesamt-Hydrauliksystem von mobilen Arbeitsmaschinen einsetzen kann, um dergestalt eine Weichenschaltung zu realisieren, mit der sich verschiedene Arbeitssektionen dann ansteuern lassen.Through the use of a switch valve according to the invention, preferably in the form of a 3/2-way valve, as a further valve of the emergency stop switch-off device instead of a "unidirectional" 2/2-way valve According to the known solution described above, the switching logic can then be expanded in such a way that the system can also be used as a kind of OR element or OR function in the overall hydraulic system of mobile work machines in order to implement a turnout that can be used then go to different work sections.

Dadurch, dass mittels des Vorsteuer-Magnetventils sowohl der hydraulische Energiefluss von der Druckversorgungsquelle zu mindestens einer der jeweiligen Arbeitssektionen als auch die Pilotdruckversorgung zu dem Steuerventil über das weitere Ventil unterbindbar ist, ist auch im Falle von drückenden oder ziehenden Lasten an den Arbeitsanschlüssen der Steuerblöcke erreicht, dass es bei Betätigen der Not-Aus-Funktion nicht noch zu ungewollten Bewegungen an den Verbrauchern kommen kann.Because both the hydraulic energy flow from the pressure supply source to at least one of the respective working sections and the pilot pressure supply to the control valve via the additional valve can be prevented by means of the pilot solenoid valve, this is also achieved in the case of pressing or pulling loads on the working connections of the control blocks that when the emergency stop function is actuated, there can still be no unwanted movements on the consumers.

Mit Hilfe von unterschiedlichen 2/2-Wege-Vorsteuer-Magnetventilen (normally open, normally closed) kann definiert werden, welche Stellung das Not-Aus-Ventil unbestromt und bestromt haben soll und welcher hydraulischer Versorgungskreis dabei aktiviert wird.With the help of different 2/2-way pilot solenoid valves (normally open, normally closed) it can be defined which position the emergency stop valve should be de-energized and energized and which hydraulic supply circuit is activated.

Mit der Ausführung Anschluss "A1" der Steuervorrichtung können zwei unterschiedliche Hydraulikkreise über das Oder-Glied wahlweise versorgt und sicherheitstechnisch vollständig entkoppelt betrieben werden. So lässt sich mit dieser Ausführung eine hydraulische Arbeitssektion mit einem hydraulischen Verbraucher ansteuern, beispielsweise in Form eines Kran- oder Hubarms mit einem hydraulisch betätigbaren Arbeitszylinders, der über ein vorgeschaltetes pilotdruckversorgtes Steuerventil von der Druckversorgung abschalt- oder abtrennbar ist, sofern das Not-Aus-Ventil (Vorsteuer-Magnetventil) betätigt eine entsprechende Weichenstellung beim Weichenventil (3/2-Wegeventil) veranlasst, das dann die hydraulische Versorgung für eine weitere hydraulische Arbeitssektion unmittelbar herstellt, die beispielsweise aus hydraulikbetätigbaren Abstützzylindern eines Mobilkrans oder dergleichen bestehen kann, die dann sicherstellen, dass im Betrieb auch unter Last der Steuervorrichtung der Mobilkran in keinem Fall umstürzen kann.With the connection "A1" version of the control device, two different hydraulic circuits can be optionally supplied via the OR link and can be operated completely decoupled from a safety point of view. This version can be used to control a hydraulic work section with a hydraulic consumer, for example in the form of a crane or lifting arm with a hydraulically actuated working cylinder, which can be switched off or disconnected from the pressure supply via an upstream pilot pressure-supplied control valve, provided the emergency stop Valve (pilot solenoid valve) actuates a corresponding switch position at the switch valve (3/2-way valve), which then directly produces the hydraulic supply for another hydraulic working section, for example can consist of hydraulically actuated support cylinders of a mobile crane or the like, which then ensure that the mobile crane cannot fall over under any circumstances even under load of the control device.

Bei der zweiten alternativen Ausführung Anschluss "T1" anstelle Anschluss "A1" können dann insbesondere Konstantpumpen-Systeme wahlweise zwischen dem internen Arbeitskreis der jeweiligen Arbeitssektionen und dem Neutralumlauf Richtung Tank oder Rücklauf T über den Anschluss "T1" geschaltet werden.In the second alternative version, connection "T1" instead of connection "A1", in particular constant pump systems can then be switched between the internal working group of the respective working sections and the neutral circulation in the direction of the tank or return flow T via the connection "T1".

Vorzugsweise wird der allgemein übliche Neutralumlauf bei Konstantpumpen-Systemen über eine Umlaufdruckwaage in der Anschlussplatte der Vorrichtung geführt und da diese je nach Ventilkonstruktion und /-auslegung immer einseitig federbelastet ist, stellt sich je nach Federvorspannung in der Regel zwischen 9 und 16 bar diese Federvorspannung in Kombination mit dem Pumpenvolumenstrom als Verlustleistung dar. Da das Weichenventil respektive das Oder-Glied keine Regelaufgaben erfüllt, sondern nur als Schaltventil ausgeführt sein soll, kann die angesprochene Federkraft demgemäß niedriger dimensioniert werden. Mit Hilfe dieser Logik lässt sich die Verlustleitung um den Faktor 3 bis 4 gegenüber herkömmlichen Systemen, wie beschrieben, reduzieren und mit der Sicherheitsabschaltung kombinieren.In the case of constant pump systems, the generally common neutral circulation is preferably carried out via a circulation pressure compensator in the connection plate of the device, and since this is always spring-loaded depending on the valve construction and design, this spring preload is generally between 9 and 16 bar depending on the spring preload Combination with the pump volume flow as power loss. Since the switch valve or the OR element does not perform any control tasks, but should only be designed as a switching valve, the spring force mentioned can accordingly be dimensioned lower. Using this logic, the loss line can be reduced by a factor of 3 to 4 compared to conventional systems as described and combined with the safety shutdown.

Vorzugsweise ist bei der erfindungsgemäßen Lösung weiter vorgesehen, dass durch eine Anordnung der Vorrichtungskomponenten mit einem Schutzfilter als erstes Glied in einer Kette vor dem Vorsteuer-Magnetventil sowohl dieses als auch gegebenenfalls eine nachgeschaltete Blendenvorrichtung, vorzugsweise in Form eines Stromreglers, gleichermaßen vor Schmutzeintrag geschützt werden, was das mögliche Ausfallrisiko der Sicherheitsfunktionen deutlich verringern hilft.It is preferably further provided in the solution according to the invention that by arranging the device components with a protective filter as the first link in a chain in front of the pilot solenoid valve, this as well as, if appropriate, a downstream orifice device, preferably in the form of a current regulator, are equally protected against the entry of dirt, which helps to significantly reduce the possible risk of failure of the safety functions.

Ferner ist vorzugsweise vorgesehen, dass nach dem Not-Aus-Abschaltventil durch einen in den hydraulischen Kreis geschalteten Messanschluss MS die Möglichkeit bestehen soll, den Druck zwischen dem Not-Aus-Ventil respektive dem Vorsteuer-Magnetventil und den jeweiligen Arbeitssektionen und somit die Schaltstellung des Not-Aus-Ventils zu überwachen. Vorzugsweise ist dabei ein weiterer Stromregler auf der Druckversorgungsseite zu den Pilotventilen des Steuerventils vorgesehen, der dazu beiträgt, dass geringe Leckagen über das Not-Aus-Ventil in Richtung Steueröl-Tankleitung Z der Pilotdruckansteuerung für das Steuerventil abgeführt werden und somit das Drucksignal an dem Messanschluss MS nicht verfälscht wird.Furthermore, it is preferably provided that after the emergency stop shut-off valve by means of a measuring connection MS connected in the hydraulic circuit, there should be the possibility of changing the pressure between the emergency stop valve or the pilot solenoid valve and the respective working sections and thus the switching position of the Monitor the emergency stop valve. A further current regulator is preferably provided on the pressure supply side to the pilot valves of the control valve, which contributes to the fact that small leaks are discharged via the emergency stop valve in the direction of the control oil tank line Z of the pilot pressure control for the control valve and thus the pressure signal at the measurement connection MS is not adulterated.

Weitere vorteilhafte Ausführungsformen der erfindungsgemäßen Steuervorrichtungslösung sind Gegenstand der Unteransprüche.Further advantageous embodiments of the control device solution according to the invention are the subject of the dependent claims.

Im Folgenden wird die erfindungsgemäße Steuervorrichtung anhand von Ausführungsbeispielen nach der Zeichnung näher erläutert. Dabei zeigen in prinzipieller Darstellung die

Fig. 1
in der Art eines hydraulischen Schaltplans die wesentlichen Komponenten der Steuervorrichtung und die
Fig. 2 und 3
geänderte Ausführungsformen für die Schaltplandarstellung nach der Fig. 1.
The control device according to the invention is explained in more detail below on the basis of exemplary embodiments according to the drawing. The basic illustration shows the
Fig. 1
in the manner of a hydraulic circuit diagram the essential components of the control device and the
2 and 3
modified embodiments for the circuit diagram display according to the Fig. 1 .

Die Fig. 1 betrifft einen Ausschnitt aus einem hydraulischen Gesamt-Schaltplan mit Darstellungen von einzelnen hydraulischen Komponenten, wie sie für solche Schaltplandarstellungen üblich sind. Im Folgenden werden die hydraulischen Schaltventile nach den Fig. 1 bis 3 jedoch nur insofern erläutert, als sie für die Erklärung der erfindungsgemäßen Steuervorrichtung notwendig sind. Die in den Figuren verwendeten Buchstaben, sofern sie zur Erläuterung der Erfindung notwendig sind, bedeuten dabei folgendes:

P
Druckversorgungsquellen-Anschluss
T
Rücklauf- oder Tank-Anschluss,
LS
Load-Sensing-Leitung,
LX
Load-Sensing-Steuerleitung,
A, B
Nutz- oder Versorgungsanschlüsse für einen hydraulischen Verbraucher (nicht dargestellt) einer Arbeitssektion,
A1
Nutz- oder Versorgungsanschluss für einen weiteren hydraulischen Verbraucher (nicht dargestellt) einer weiteren Arbeitssektion,
T1
Anschluss für einen Neutralumlauf Richtung Tank oder Rücklauf T,
MS
Messanschluss für einen Druckwertaufnehmer PI,
Z, C
Steuerleitungen für eine Vorsteuerdruckerzeugung für Pilotventile eines Steuerventils,
MP, MY, PC
weitere hydraulische Anschlussstellen.
The Fig. 1 relates to a section of an overall hydraulic circuit diagram with representations of individual hydraulic components, as are customary for such circuit diagram representations. In the following, the hydraulic switching valves according to the 1 to 3 however only insofar explained as they are necessary for the explanation of the control device according to the invention. The letters used in the figures, insofar as they are necessary to explain the invention, mean the following:
P
Pressure supply source connection
T
Return or tank connection,
LS
Load sensing line,
LX
Load sensing control line,
A, B
Utility or supply connections for a hydraulic consumer (not shown) of a working section,
A1
Utility or supply connection for a further hydraulic consumer (not shown) of a further working section,
T1
Connection for a neutral circulation towards the tank or return T,
MS
Measuring connection for a pressure transducer PI,
Z, C
Control lines for pilot pressure generation for pilot valves of a control valve,
MP, MY, PC
further hydraulic connection points.

Die zugehörige Anschlussstelle P einer üblichen Druckversorgungsquelle lässt sich wiederum in üblicher Weise mit Fluid vorgebbaren Drucks von einer Konstant- oder Verstellpumpe (nicht dargestellt) versorgen. Ausgehend von der Anschlussstelle P mit der Druckversorgungsquelle endet eine Pumpenleitung 10 jeweils auf der Eingangsseite einer Umlaufdruckwaage 12, eines Weichenventils 14 sowie eines Vorsteuer-Magnetventiles 16. Auf der Ausgangsseite der jeweiligen Ventileinrichtung 12, 16 münden diese in eine Rücklauf- oder Tankleitung ein, die zum Rücklauf- oder Tankanschluss T führt. Bei der Ausführungsform nach der Fig. 3, also bei der Ausführung T1, mündet auch die Ausgangsseite des Ventils 14 in die Rücklauf- oder Tankleitung ein. Sofern in den Figuren die Leitungen strichliniert wiedergegeben sind, soll dies verdeutlichen, dass sie zum Ansteuern von entsprechend angeschlossenen hydraulischen Komponenten dienen.The associated connection point P of a conventional pressure supply source can in turn be supplied in the usual manner with fluid that can be predetermined by a constant or variable displacement pump (not shown). Starting from the connection point P with the pressure supply source, a pump line 10 ends on the input side of a circulation pressure compensator 12, a switch valve 14 and a pilot solenoid valve 16. On the output side of the respective valve device 12, 16, these open into a return line or tank line, which leads to the return or tank connection T. In the embodiment according to the Fig. 3 , that is to say in the T1 version, the outlet side of the valve 14 also opens into the return line or tank line. If the lines are shown in dashed lines in the figures , this should make it clear that they are used to control correspondingly connected hydraulic components.

Die Umlaufdruckwaage 12 ist mit ihren beiden einander gegenüberliegenden Steuerseiten an Steuerleitungen angeschlossen, die über die Pumpenleitung 10 versorgt sind, wobei in Blickrichtung auf die Fig. 1 gesehen die obere Steuerleitung über eine Blende oder Drossel 20 an die Pumpenleitung 10 angeschlossen ist. Im Übrigen wird die Umlaufdruckwaage 12 federunterstützt in ihrer in der Fig. 1 gezeigten Schließ- oder Sperrstellung im unangesteuerten Zustand gehalten. Sofern in der Schaltplandarstellung rechteckförmige Kästchen gezeigt sind, die von einer Fluidleitung oder Fluiddurchgangsstelle durchgriffen sind, handelt es sich um sogenannte Leer- oder Platzhalter, die im Bedarfsfall mit weiteren hydraulischen Komponenten bestückbar sind.The circulation pressure compensator 12 is connected with its two opposite control sides to control lines which are supplied via the pump line 10, with a view towards the Fig. 1 seen the upper control line is connected to the pump line 10 via an orifice or throttle 20. In addition, the circulation pressure compensator 12 is spring-supported in its in the Fig. 1 shown closed or locked position held in the uncontrolled state. If rectangular diagrams are shown in the circuit diagram that are penetrated by a fluid line or fluid passage point, they are so-called empty or placeholders that can be equipped with further hydraulic components if necessary.

In Blickrichtung auf die Fig. 1 gesehen und entsprechend hydraulisch nachgeschaltet ist das Weichenventil 14 vorhanden, das als 3/2-Wege-Schaltventil konzipiert ist und vom Verständnis der Schaltlogik her eine Art "Oder-Glied" ausbildet. In der in der Fig. 1 gezeigten federbelasteten Grundstellung stellt das Weichenventil 14 eine fluidführende Verbindung zwischen der Pumpenleitung 10 und dem Anschluss A1 her. Die beiden gegenüberliegenden Steuerleitungen für das Weichenventil 14 sind wiederum an die Pumpenleitung 10 angeschlossen, wobei in Blickrichtung auf die Fig. 1 gesehen in die untere Steuerleitung eine Blende oder Drossel 22 geschaltet ist. Wird das Weichenventil 14 fluidangesteuert betätigt, wird entgegen der Wirkung der Federkraft eine fluidführende Verbindung zwischen der druckführenden Pumpenleitung 10 in Richtung der Anschlussstellen A oder B hergestellt, was im Folgenden noch näher erläutert werden wird.Looking towards the Fig. 1 seen and hydraulically connected accordingly, the switch valve 14 is present, which is designed as a 3/2-way switching valve and from the understanding of the switching logic forms a kind of "OR element". In the in the Fig. 1 shown spring-loaded basic position, the switch valve 14 establishes a fluid-carrying connection between the pump line 10 and the connection A1. The two opposite control lines for the switch valve 14 are in turn connected to the pump line 10, looking in the direction of the Fig. 1 seen in the lower control line, an aperture or throttle 22 is connected. If the switch valve 14 is actuated in a fluid-controlled manner, a fluid-carrying connection between the pressure-carrying pump line 10 in the direction of the connection points A or B is established against the action of the spring force, which will be explained in more detail below.

Wiederum in Übereinanderanordnung und hydraulisch nachgeschaltet, ist das Vorsteuer-Magnetventil 16 vorgesehen, das federbelastet in seiner gezeigten Sperrstellung oder "normally closed"-Stellung gezeigt ist. Wird das Ventil 16 magnetbetätigt geschaltet, gelangt es in seine geöffnete Stellung und stellt eine Fluidverbindung zwischen der Pumpenleitung 10 und der Rücklauf- oder Tankleitung 18 her. Zwischen den beiden Eingangsseiten der Ventile 14, 16 ist ein Schutzfilter 24 sowie ein Stromregler 26 geschaltet. Zwischen Schutzfilter 24 und Stromregler 26 mündet von der Pumpenleitung 10 aus gesehen eine Anschlussstelle MP aus dem strichpunkiert dargestellten Steuerblock 30 der Steuervorrichtung aus. Innerhalb des genannten Steuerblocks 30 ist wiederum strichpunktiert ein Block 32 dargestellt, der die wesentlichen Komponenten der Not-Aus-Abschalteinrichtung umfasst, bestehend insbesondere aus dem Weichenventil 14, dem Vorsteuer-Magnetventil 16 sowie dem Schutzfilter 24 und dem Stromregler 26.Again arranged one above the other and hydraulically connected, the pilot solenoid valve 16 is provided, which is shown spring-loaded in its shown blocking position or "normally closed" position. If the valve 16 is switched solenoid operated, it reaches its open position and establishes a fluid connection between the pump line 10 and the return line or tank line 18. A protective filter 24 and a current regulator 26 are connected between the two input sides of the valves 14, 16. Between the protective filter 24 and the current regulator 26, a connection point MP opens out of the control block 30 of the control device, shown in broken lines, as seen from the pump line 10. Within the control block 30 mentioned, a block 32 is again shown in broken lines, which comprises the essential components of the emergency stop switch-off device, consisting in particular of the switch valve 14, the pilot solenoid valve 16 and the protective filter 24 and the current regulator 26.

Für die Ansteuerung der beiden Anschlüsse A, B dient ein übliches und daher nicht mehr näher beschriebenes pilotdruckversorgtes Steuerventil 34, das in der Fig. 1 in seiner gesperrten Ventilschieberstellung gezeigt ist mit einer eingangsseitigen Anschlussstelle, die über ein Wechselventil 36 an die Load-Sensing-Leitung LS angeschlossen ist. Gelangt der Ventilschieber des Steuerventils 34 in seine in Blickrichtung auf die Fig. 1 gesehen untere Schaltposition, wird bei entsprechend betätigtem Weichenventil 14 der Versorgungs- oder Pumpendruck in der Pumpenleitung 10 über die abgabeseitig an das Weichenventil 14 angeschlossene Versorgungsleitung 38 sowie das Steuerventil 34 ausgangsseitig des Steuerventils 34 an den Nutzanschluss A weitergegeben, wohingegen der Nutzanschluss B über das Steuerventil 34 in dieser Schaltstellung an den Rücklauf oder Tankanschluss T angeschlossen ist. Gelangt der Steuerschieber des Ventils 34 in seine in der Fig. 1 gezeigte obere Stellung, wird der Nutzanschluss B mit dem Pumpendruck versorgt und der Nutzanschluss A wird auf Rücklauf oder Tank T geschaltet. Zum Ansteuern des federbelasteten Steuerventilschiebers des Ventils 34 dienen zwei Pilotventile 40, die jeweils über eine eigenständige Ansteuerung über die Steuerleitungen Z, C verfügen, von denen der Einfachheit halber aber die Fluidführung nur für ein Pilotventil 40 dargestellt ist, indem die Steuerleitung Z zu dem einen Pilotventil führt und die weitere Steuerleitung C zu dem anderen Pilotventil 40.A conventional pilot pressure-supplied control valve 34, which is shown in FIG Fig. 1 is shown in its blocked valve slide position with an input-side connection point which is connected to the load-sensing line LS via a shuttle valve 36. The valve spool of the control valve 34 reaches in its direction of view Fig. 1 seen lower switching position, the supply or pump pressure in the pump line 10 is passed on via the supply line 38 connected to the output side to the switch valve 14 and the control valve 34 on the output side of the control valve 34 to the useful port A, whereas the useful port B via the control valve 34 is connected to the return or tank connection T in this switching position. If the control slide of the valve 34 in its Fig. 1 shown upper position, the service port B is supplied with the pump pressure and the service port A is switched to return or tank T. To control the spring-loaded control valve spool of the valve 34 serve two pilot valves 40, each of which has its own control via the control lines Z, C, of which, however, for the sake of simplicity, the fluid flow is only shown for one pilot valve 40, in that the control line Z leads to the one pilot valve and the further control line C. to the other pilot valve 40.

In die Steueröl-Tankleitung der Steuerleitung Z für das jeweilige Pilotventil 40 mündet ebenfalls eine Anschlussleitung 42, in die vorzugsweise ein weiterer Stromregler 44 in Form eines Ventils geschaltet ist, wobei die Anschlussleitung 42 an einer Abzweigstelle 46 mit der Versorgungsleitung 38 verbunden ist. Des Weiteren ist die Steuerleitung Z über ein Druckbegrenzungsventil 48 und über die Blende oder Drossel 20 permanent fluidführend an die druckversorgende Pumpenleitung 10 angeschlossen. Eine Filtereinrichtung 50 nebst einem weiteren Druckregelventil 52 dient der internen Vorsteuerdruckerzeugung für die Pilotventile 40 im Rahmen der elektrohydraulischen Schieberbetätigung für die einzelnen Arbeitssektionen. Das weitere Druckregelventil 52 ist dabei ausgangsseitig an die weitere Steuerleitung C angeschlossen. Die Steuerleitungen Z, C sind am Ausgang des Steuerblocks 30 in entsprechende Anschlussstellen Z, C einmündend dargestellt. Ebenso ist die Load-Sensing-Leitung LS ausgangsseitig am Block 30 in die Anschlussstelle LS ausmündend dargestellt.A connection line 42 also opens into the control oil tank line of the control line Z for the respective pilot valve 40, into which a further current regulator 44 in the form of a valve is preferably connected, the connection line 42 being connected to the supply line 38 at a branch point 46. Furthermore, the control line Z is permanently connected to the pressure-supplying pump line 10 via a pressure limiting valve 48 and via the orifice or throttle 20. A filter device 50 together with a further pressure control valve 52 is used for internal pilot pressure generation for the pilot valves 40 as part of the electro-hydraulic slide valve actuation for the individual working sections. The further pressure control valve 52 is connected on the output side to the further control line C. The control lines Z, C are shown at the output of the control block 30 opening into corresponding connection points Z, C. Likewise, the load-sensing line LS is shown on the output side at block 30 opening into the connection point LS.

Auf der Eingangsseite des Steuerventils 34 ist die Versorgungsleitung 38 in ein Stromregelventil 54 einmündend dargestellt, das von einem Load-Sensing-Druck des Steuerventils 34, wie dargestellt, angesteuert ist. Ferner mündet die Versorgungsleitung 38 in Blickrichtung auf die Fig. 1 gesehen an ihrem unteren Ende in einen Messanschluss MS aus, an den ein PI-Druckwertaufnehmer 56 anschließbar ist.On the input side of the control valve 34, the supply line 38 is shown opening into a flow control valve 54 which is controlled by a load-sensing pressure of the control valve 34, as shown. Furthermore, the supply line 38 opens out in the direction of viewing Fig. 1 seen at its lower end in a measuring connection MS, to which a PI pressure sensor 56 can be connected.

Bei dem gezeigten Ausführungsbeispiel nach der Fig. 1 soll an den Anschlussstellen A, B unter Bildung einer ersten hydraulischen Arbeitssektion ein nicht näher dargestellter hydraulischer Arbeitszylinder mit seinen beiden Fluid- oder Arbeitsräumen angeschlossen sein, wobei der Arbeitszylinder den Kran- oder Hubarm eines Mobilkrans ansteuern soll. An die Anschlussstelle A1 ist eine weitere hydraulische Arbeitssektion angeschlossen, welche wiederum hydraulische Stützzylinder versorgt, die entsprechend ausgefahren die Plattform des Mobilkrans stabilisieren, damit dieser auch im Betrieb nicht umfallen oder an einer Seite einknicken kann. Die genannte Verwendung der Steuervorrichtung ist nur beispielhaft; andere sinnfällige Einsatzmöglichkeiten sind denkbar.In the embodiment shown according to the Fig. 1 should at the connection points A, B with the formation of a first hydraulic working section a hydraulic working cylinder, not shown, can be connected with its two fluid or working spaces, the working cylinder being intended to control the crane or lifting arm of a mobile crane. A further hydraulic working section is connected to the connection point A1, which in turn supplies hydraulic support cylinders which, when extended, stabilize the platform of the mobile crane so that it cannot fall over or buckle on one side during operation. The use of the control device mentioned is only exemplary; other possible uses are conceivable.

Wird das Vorsteuerventil 16 betätigt, also in seine Fluid durchlassende Stellung gebracht, schaltet das Weichenventil 14 in seine untere Schaltstellung und versorgt dann mit Pumpendruck über die Pumpenleitung 10, wie bereits beschrieben, das jeweils zuordenbare Pilotventil 40, was zu einer entsprechenden Auslenkung des Steuerschiebers des Steuerventils 34 führt und die Anschlussstellen A oder B der ersten hydraulischen Arbeitssektion werden mit Fluid vorgebbaren Drucks zur Betätigung derselben versorgt. Wird nun das Vorsteuerventil 16 nicht betätigt und gelangt in seine gezeigte, normalerweise geschlossene Stellung, wird das Weichenventil 14 federbetätigt in seine in Fig. 1 gezeigte Stellung gebracht und es folgt dann ausschließlich eine Fluidversorgung unter Druck über die Pumpenleitung 10 in Richtung der Anschlussstelle A1 mit der weiteren hydraulischen Arbeitssektion.If the pilot valve 16 is actuated, i.e. brought into its fluid-permitting position, the switch valve 14 switches to its lower switching position and then supplies the respective pilot valve 40 with pump pressure via the pump line 10, as already described, which leads to a corresponding deflection of the control slide of the Control valve 34 leads and the connection points A or B of the first hydraulic working section are supplied with fluid pressure that can be predetermined to actuate the same. If the pilot valve 16 is not actuated and reaches its normally closed position shown, the switch valve 14 is spring actuated into its in Fig. 1 brought position shown and then follows only a fluid supply under pressure via the pump line 10 in the direction of the connection point A1 with the further hydraulic working section.

Im aufgezeigten Anwendungsbeispiel mit dem Mobilkran werden dann die Stützzylinder für die Plattform des Mobilkrans entsprechend versorgt, was der Sicherheit dient, da diese dann ihre Stützfunktion wahrnehmen können. Andererseits ist dann die Versorgungsleitung 38 von der Druckversorgung her abgesperrt, was dazu führt, dass das jeweilige Pilotventil 40 nicht mehr angesteuert wird und mithin der Ventilschieber des Steuerventils 34 federunterstützt in seine sperrende Grundstellung gelangt gemäß der Darstellung nach der Fig. 1 und damit mit Sicherheit die Fluidversorgung für die erste hydraulische Arbeitssektion mit der Versorgung über die jeweiligen Nutzanschlüsse A oder B unterbindet.In the application example shown with the mobile crane, the support cylinders for the platform of the mobile crane are then supplied accordingly, which serves for safety, since they can then perform their support function. On the other hand, the supply line 38 is then shut off from the pressure supply, which means that the respective pilot valve 40 is no longer actuated and the valve slide of the control valve 34 thus reaches its blocking basic position with spring support, as shown after Fig. 1 and thus surely prevents the fluid supply for the first hydraulic working section with the supply via the respective service connections A or B.

Bei entsprechend betätigter Not-Aus-Funktion über die zugehörige Abschalteinrichtung 32 ist dann selbst bei ziehenden oder drückenden Lasten in der ersten Arbeitssektion mit Sicherheit die Versorgung derart unterbunden, dass der jeweils in der ersten Arbeitssektion angeschlossene hydraulische Verbraucher sich nicht mehr bewegen kann. Mit nur einem Magnetventil 16 kann also gleichzeitig der hydraulische Energiefluss von der Druckversorgung zu der jeweils ersten Arbeitssektion als auch die Pilotdruckversorgung der elektro-hydraulischen Steuerschieberansteuerung für das Steuerventil 34 unterbrochen werden, was so keine Entsprechung im Stand der Technik hat.When the emergency stop function is actuated appropriately via the associated shutdown device 32, the supply is reliably prevented in the first working section, even with pulling or pushing loads, in such a way that the hydraulic consumer connected in the first working section can no longer move. With only one solenoid valve 16, the hydraulic energy flow from the pressure supply to the respective first working section as well as the pilot pressure supply of the electro-hydraulic control slide control for the control valve 34 can be interrupted at the same time, which has no correspondence in the prior art.

Anstelle des Magnetventils 16 gemäß der Darstellung nach der Fig. 1, das im Normalfall geschlossen ist (normally closed), kann auch optional im Bedarfsfall ein anderes Vorsteuer-Magnetventil eingesetzt werden, das in der Grundstellung normalerweise geöffnet ist (normally open) und betätigt in seine geschlossene Sperrstellung gelangt. Je nach Art des dann eingesetzten Vorsteuerventils 16 kann dann entschieden werden, welche Stellung das Not-Aus-Ventil 14 unbestromt oder bestromt haben soll und welcher Kreis mit den hydraulischen Arbeitssektionen (A, B, A1) aktiviert wird. Durch die Anordnung mit dem Schutzfilter 24 und dem hydraulisch nachgeschalteten Stromregler 26 als Blendenvorrichtung lässt sich das jeweilige Vorsteuer-Magnetventil 16 sicher vor Schmutzeintrag schützen, was das mögliche Ausfallrisiko der benötigten Sicherheitsfunktion wesentlich reduzieren hilft.Instead of the solenoid valve 16 as shown in the Fig. 1 which is normally closed, another pilot solenoid valve can optionally be used if necessary, which is normally open in the basic position (normally open) and actuated to its closed blocking position. Depending on the type of pilot valve 16 then used, it can then be decided which position the emergency stop valve 14 should be deenergized or energized and which circuit is activated with the hydraulic working sections (A, B, A1). Due to the arrangement with the protective filter 24 and the hydraulically connected current regulator 26 as an orifice device, the respective pilot solenoid valve 16 can be reliably protected from dirt, which helps to significantly reduce the possible failure risk of the required safety function.

Auf der Ausgangsseite des Not-Aus-Abschaltventils in Form des Wechselventils 36 besteht durch den Messanschluss MS die Möglichkeit, den anstehenden Druck zwischen dem Ventil 14 und den angesteuerten Arbeitssektionen und somit die Schaltstellung des Not-Aus-Ventils 14 zu überwachen. Der weitere Stromregler 44 trägt dann mit dazu bei, dass etwaig gering auftretende Leckagemengen über das Not-Aus-Ventil 14 in Richtung der Steueröl-Tankleitung über die Steuerleitung Z abgeführt werden können und somit das Drucksignal an dem Messanschluss MS nicht verfälscht wird.On the output side of the emergency shutdown valve in the form of the shuttle valve 36 there is the possibility, through the measuring connection MS, of the pressure present between the valve 14 and the controlled working sections and thus to monitor the switching position of the emergency stop valve 14. The further current controller 44 then contributes to the fact that any small amounts of leakage that occur can be discharged via the emergency stop valve 14 in the direction of the control oil tank line via the control line Z and thus the pressure signal at the measurement connection MS is not falsified.

Die Fig. 2 gibt zur verbesserten Darstellung die Verhältnisse des Steuerblocks 30 in Blickrichtung links von dem Steuerventil 34 wieder. Die bisher getroffenen Ausführungen gelten auch insoweit für die hydraulischen Komponenten nach der Fig. 2.The Fig. 2 shows the conditions of the control block 30 in the direction of view to the left of the control valve 34 for improved illustration. The statements made so far also apply to the hydraulic components according to the Fig. 2 .

Die Fig. 3 entspricht wiederum der Darstellung nach der Fig. 2 mit der Maßgabe, dass an dem Messanschluss MS nicht der PI-Druckwertaufnehmer 56 gezeigt ist und anstelle des Anschlusses A1 für eine weitere hydraulische Arbeitssektion ist die entsprechende Anschlussstelle mit der Bezeichnung T1 abgewandelt, was die Möglichkeit eröffnet, speziell für den Einsatz von Konstant-Pumpensystemen wahlweise zwischen dem internen Arbeitskreis der jeweiligen Arbeitssektion und dem Neutralumlauf in Richtung Rücklauf- oder Tankanschluss T über den Anschluss T1 gemäß der Darstellung nach der Fig. 3 zu wählen. Dabei erfolgt allgemein der übliche Neutralumlauf bei den genannten Konstantpumpensystemen über die bereits beschriebene Umlaufdruckwaage 12, die, wie dargestellt, immer einseitig federbelastet ist und je nach Federvorspannung, in der Regel zwischen 9 und 16 bar, ergibt sich hieraus in Kombination mit dem Pumpenvolumenstrom eine Verlustleistung. Da das Weichenventil 14 in Form des Oder-Gliedes keine Regelaufgaben erfüllen muss, sondern nur als einfaches Schaltventil ausgeführt zu werden braucht, kann demgemäß die Federkraft für die Umlaufdruckwaage 12 niedriger dimensioniert werden. Dergestalt lässt sich die Verlustleistung um den Faktor 3 bis 4 gegenüber herkömmlichen Systemen reduzieren und mit der Sicherheitsschaltung kombinieren.The Fig. 3 again corresponds to the representation according to Fig. 2 with the proviso that the PI pressure sensor 56 is not shown on the measurement connection MS and instead of the connection A1 for a further hydraulic working section, the corresponding connection point with the designation T1 has been modified, which opens up the possibility, especially for the use of constant pump systems either between the internal working group of the respective working section and the neutral circulation in the direction of the return or tank connection T via the connection T1 as shown in the figure Fig. 3 to choose. In general, the usual neutral circulation in the above-mentioned constant pump systems takes place via the circulation pressure compensator 12 already described, which, as shown, is always spring-loaded on one side and, depending on the spring preload, generally between 9 and 16 bar, results in a power loss in combination with the pump volume flow . Since the switch valve 14 in the form of the OR element does not have to perform any control tasks, but only has to be designed as a simple switching valve, the spring force for the circulating pressure compensator 12 can accordingly be dimensioned lower. In this way, the power loss can be reduced by a factor of 3 to 4 compared to conventional systems and combined with the safety circuit.

Claims (9)

  1. Control device for at least two hydraulic work sections (A, A1, B), with a control block (30), which comprises at least one service port (A, A1, B) for the respective hydraulic work section, a pressure supply source port (P), a return port (T), a hydraulic supply circuit, a pilot pressure-supplied control valve (34) and an emergency shutdown device (32), one hydraulic work section being able to be connected via the hydraulic supply circuit and the pilot pressure-supplied control valve (34) to a pressure supply source (P) and a return (T), the emergency shutdown device (32) comprising a pilot solenoid valve (16) and a further valve (14), both the hydraulic energy flow from the pressure supply source port (P) to at least one of the respective work sections (A, B) via the respective service port (A, B) and the pilot pressure supply to the control valve (34) via the further valve (14) being able to be blocked by means of the pilot solenoid valve (16), characterised in that the emergency shutdown device (32), in addition to the pilot solenoid valve (16), has a switch valve as a further valve (14), said switch valve acting as a kind of OR gate depending on the actuation status of the pilot solenoid valve (16), making it possible to selectively supply fluid in a non-actuated emergency shutdown function at least to one hydraulic work section (A, B) via the respective service port (A, B) and in an actuated emergency shutdown function at least to one further hydraulic work section (Al, T1) via the respective service port (A1, T1).
  2. Control device according to claim 1 characterised in that the switch valve (14) is a 3/2-way valve.
  3. Control device according to either claim 1 or claim 2, characterised in that the service port (A1, T1) for the respective further hydraulic work section can selectively supply a further assignable hydraulic load or permits a neutral circulation in the direction of the return (T).
  4. Control device according to any one of the preceding claims, characterised in that the control block (30) comprises a pump line (10) from the pressure supply source port (P), and a circulation pressure compensator (12) is connected in the pump line (10) to the input side of the switch valve (14) in front of said input side.
  5. Control device according to any one of the preceding claims, characterised in that the pilot solenoid valve (16) is connected downstream of the input side of the switch valve (14), said solenoid valve being designed as a 2/2-way valve and being optionally blocked in its initial position or switched such as to allow fluid to pass through.
  6. Control device according to any one of the preceding claims, characterised in that a current regulator (26) is connected between the input side of the switch valve (14) and the input side of the pilot solenoid valve (16).
  7. Control device according to claim 6, characterised in that a protective filter (24) is connected between the input side of the switch valve (14) and the input side of the current regulator (26).
  8. Control device according to any one of the preceding claims, characterised in that a measurement port (MS) is connected on the output side of the switch valve (14) in the direction of the pressure supply for the service port (A,B) of the at least one hydraulic work section (A, B) in front of the input side of the control valve (34).
  9. Control device according to any one of the preceding claims, characterised in that a further current regulator (44) is connected on the output side of the switch valve (14) in the direction of the pressure supply for the pilot valves (40) of the control valve (34).
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WO2017167435A1 (en) 2017-10-05
EP3436705A1 (en) 2019-02-06
US20200340499A1 (en) 2020-10-29
DE102016003972A1 (en) 2017-10-05
US10962031B2 (en) 2021-03-30

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