EP1253327B1 - Hydraulic control circuit - Google Patents

Hydraulic control circuit Download PDF

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Publication number
EP1253327B1
EP1253327B1 EP02008997A EP02008997A EP1253327B1 EP 1253327 B1 EP1253327 B1 EP 1253327B1 EP 02008997 A EP02008997 A EP 02008997A EP 02008997 A EP02008997 A EP 02008997A EP 1253327 B1 EP1253327 B1 EP 1253327B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
valve
control device
throttle
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.)
Expired - Lifetime
Application number
EP02008997A
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German (de)
French (fr)
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EP1253327A1 (en
Inventor
Wölfgang Kötter
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165Servomotor 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/20Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205Systems with pumps
    • F15B2211/2053Type of pump
    • F15B2211/20538Type of pump constant capacity
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/20Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205Systems with pumps
    • F15B2211/2053Type of pump
    • F15B2211/20546Type of pump variable capacity
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/20Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25Pressure control functions
    • F15B2211/253Pressure margin control, e.g. pump pressure in relation to load pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30525Directional control valves, e.g. 4/3-directional control valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/3056Assemblies of multiple valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/315Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157Directional 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
    • F15B2211/31576Directional 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/35Directional control combined with flow control
    • F15B2211/351Flow control by regulating means in feed line, i.e. meter-in control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/405Flow control characterised by the type of flow control means or valve
    • F15B2211/40507Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/42Flow control characterised by the type of actuation
    • F15B2211/426Flow control characterised by the type of actuation electrically or electronically
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/47Flow control in one direction only
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/505Pressure control characterised by the type of pressure control means
    • F15B2211/50563Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/51Pressure control characterised by the positions of the valve element
    • F15B2211/513Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/515Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an output member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/52Pressure control characterised by the type of actuation
    • F15B2211/528Pressure control characterised by the type of actuation actuated by fluid pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/605Load sensing circuits
    • F15B2211/6051Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/605Load sensing circuits
    • F15B2211/6051Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/63Electronic controllers
    • F15B2211/6303Electronic controllers using input signals
    • F15B2211/6306Electronic controllers using input signals representing a pressure
    • F15B2211/6309Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/63Electronic controllers
    • F15B2211/6303Electronic controllers using input signals
    • F15B2211/6306Electronic controllers using input signals representing a pressure
    • F15B2211/6313Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/63Electronic controllers
    • F15B2211/6303Electronic controllers using input signals
    • F15B2211/6333Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention is based on a hydraulic control device according to the specified in the preamble of claim 1 in more detail Genus.
  • A1 hydraulic LS control device a control line goes through directional control valves through and leads via shuttle valves to a pressure medium supply device.
  • a 2/2 way on-off valve is in between one of a pressure medium supply device with a variable pump outgoing inlet channel and the Pressure medium supply device closest control line section the control line and a flow control valve is between this control line section and a return channel connected.
  • the flow control valve is only for a small Oil flow designed, not only after the switching of the Zuschaltventils in transit position, but also in normal Operation of the control device continuously the regulated oil flow, on which the flow control valve is set, from the control line flows into the return channel and the regulated oil flow insofar represents a leakage current, the smallest possible should be kept.
  • a hydraulic control device with the features of the The preamble of claim 1 is known from DE 195 42 371 A1 known.
  • this control device is a pressure compensator in a connection plate of a constant pump with pressure medium supplied and via a control circuit with the selected maximum load pressure of the simultaneously actuated hydraulic Consumers charged to a so-called LS control to reach.
  • LS control so-called LS control to reach.
  • Such use cases are, for example, the load of the working hydraulics in a tractor at take-off to warm up the oil, or a braking function in a hydrostatic drive, if, for example, in a forklift the engine is braked when driving while the throttle is removed.
  • the rule-pressure drop at the directional control valve when the valve spool is actuated be as small as possible To avoid loss of energy.
  • the end plate an electromagnetically actuated 3/2-Zuschaltventil on, at its three terminals one Inlet channel, a return channel and a control channel of a Control circuit are connected.
  • valve in the end plate can be the pressure compensator in the Activate working hydraulics, giving them a pressure accumulated, which corresponds to the system pressure or with Help of a second, not shown pilot pressure relief valve lower than the system pressure can be set.
  • This Solution is poorly suited for a control device in which Instead of a constant pump, a variable displacement pump for Pressure medium supply is used. Also builds this solution with its three-port on-off valve relative consuming. In addition, this design is not very variable and therefore less suitable for special applications, such as proportional adjustment in a control loop.
  • the inventive hydraulic control device with the Characteristic features of claim 1 has the other hand the advantage that they are versatile in simpler construction is applicable. Above all, she is suitable for different pressure medium supply devices, at who once used a constant pump with pressure compensator can be, while in the other case with a variable Regulator is applicable. In this case, the control device requires Relatively little extra valve effort, so they compact and inexpensive builds. Through the special tap the LS pressure between the connection valve and throttle can the Pressure build-up with activated connection valve up to the maximum System pressure done. Relief of the control line in LS control circuit at rest is maintained. Further gives rise to the functional advantage that the load is easily determinable with the help of the throttle.
  • FIG. 1 shows a first one Embodiment of the hydraulic control device with Constant pump in a simplified representation
  • Figure 2 a second embodiment of the control device with Variable displacement pump in a simplified representation.
  • FIG. 1 shows a first hydraulic control device 10, in the multi-way valves 11, 12, 13, 14 for control of unspecified hydraulic consumers are provided. That for a single-acting function provided directional control valve 11 and for a double-acting Function provided directional valves 12 to 14 are connected to each other flanged and between a connection plate 15 and a End plate 16 is arranged so that it has a directional control valve block 17 form.
  • the directional control valve block 17 is of a Constant pump 18 supplied with pressure medium, wherein of a 19 designated inlet connection in the connection plate 15th an inlet channel 21 goes out, the connecting plate 15 and all directional valves 11 to 14 penetrates and the end plate 16 leads. At this inlet channel 21 all valves 11 to 14 connected in parallel. Furthermore, the connection plate 15 to a return port 22, with an all Directional valves 11 to 14 penetrating return channel 23 in Connection stands and the via a return line 24 to a tank 25 is relieved.
  • connection plate 15 In the connection plate 15 is the inlet port 19 via a bypass line 26 with the return port 22 in Connection, wherein in this bypass line 26 a pressure balance 27 is switched.
  • the pressure compensator 27 is in itself known manner on the one hand from the delivery pressure of Constant pump 18 pressurized while on the other Side of a control spring 28 and the signal pressure from a Control circuit 29 is acted upon.
  • a pressure relief valve 31 is provided, which is connected in the control circuit 29 and together with the pressure compensator 27 as a pilot-operated pressure relief valve for the system pressure in the first controller '10 serves.
  • FIG. 1 also shows, all directional control valves 11 to 14 in a conventional manner for a load pressure compensated Control is formed, also called LS control referred to as.
  • LS control a load pressure compensated Control
  • the control circuit 29 is thus the respective maximum load pressure of one of the operated directional control valves 11 to 14 tapped and with this Signal pressure the pressure compensator 27 acted upon.
  • a Transverse channel 35 is arranged, via which the inlet channel 21 from adjacent directional control valve 14 with the return channel 23rd the same directional valve 14 is connected.
  • the Zuschaltventil 36 is here as simple 2/2 valve designed. It is also appropriate the throttle 37 adjustable form ..
  • the second, continuous control line 34 with its farthest from the terminal plate 15, last section to the transverse channel 35 so connected that the signal pressure between the Zuschaltventil 36 and the downstream thereof Throttle 37 picks up.
  • the two components Zuschaltventil 36 and adjustable throttle 37 are thus both in Working group and are designed accordingly large.
  • the fixed displacement pump 18 and the pressure compensator 27 form one here Pressure medium supply device 38 for the first Control device 10.
  • control device 10 of Figure 1 The operation of the control device 10 of Figure 1 is as explained below, the basic function of a load pressure compensated control as known per se is assumed.
  • Control device 10 addition to an additional function of Work hydraulics may be desirable by the hydraulic Performance of a pressurized and piped tank Volume flow is used, so this can be independent of the Actuation of the directional valves 11 to 14 with the help of Zuschaltventils 36 can be achieved.
  • Such an extra Function may be desired in many cases, e.g. if by the load of the working hydraulics in a tractor When starting, the oil should be heated.
  • Another Use case results in a forklift with Internal combustion engine and hydrostatic drive in the Driving should be slowed down when removing the gas.
  • the directional valves 11 to 14 are in their respective middle positions while that aroused Zuschaltventil 36 assumes its open position.
  • the one of the Constant pump 18 funded pressure medium flow can therefore via the inlet channel 21 and the open connection valve 36, over the transverse channel 35 and the throttle 37 in the Return channel 23 and flow to the tank 25.
  • the one of the Throttle 37 built-up dynamic pressure in the transverse channel 35 is about the second control line 34 tapped and on the spring-loaded end face of the pressure compensator 27 out. But this is the pressure compensator 27 is short-circuited and the Constant pump 18 can build up a pressure on the am Pressure relief valve 31 set system pressure reached.
  • the Zuschaltventil 36 is thus the Pressure compensator 27 is activated so that the circulation pressure Substantially exceeding pressure is reached, which is up to Level of the set system pressure can lead.
  • the throttle 37 can be the back pressure in the inlet channel adjust, and thus the burden of Working hydraulics. In the control device 10 can Thus, with the help of the Zuschaltventils 36 a burden of Working hydraulics can be achieved as additional Function is usable.
  • FIG. 2 shows a simplified embodiment of a second control device 40 extending from the first Control device 10 according to Figure 1, especially by a another, second pressure medium supply device 41 different.
  • This second Pressure medium supply device 41 has a Variable 42 and an associated control valve 43, wherein for limiting the system pressure the control valve 43, the Pressure relief valve 31 is assigned.
  • the Connection plate 15 can therefore account for a pressure balance, while the end plate 16 remains unchanged in construction. Instead of the previous way valves 11 to 14 are only three-way valves 11 to 13 shown.
  • the second control device 40 also has a first Sensor 44 which in the return channel 23 of the Connection plate 15 the temperature of the outflowing Pressure medium flow measures and sends its signals to a electronic control unit 45 reports. Furthermore, in the second pressure medium supply device 41 a second Sensor 46 is provided, the speed of the variable 42nd determined and dependent signals to the control unit 45 passes. Furthermore, at the electronic Control unit 45, a first setpoint input 47 is provided, with a desired temperature of the pressure medium flow or whose maximum temperature can be specified. At a second setpoint input 48, setpoints for the Speed of the variable 42 input. The electronic Control unit 45 determined from the entered desired and Actual values are a control deviation and thus controls one Actuator 49, with which the adjustable throttle 37 in the end plate 16 is actuated.
  • the operation of the second control device 40 with the Variable 42 for pressure medium supply corresponds to Substantially that of the first control device 10 after Figure 1.
  • the help of the first Sensor 44 detected temperature of the outflowing Pressure fluid flow in the return channel 23 and with at the Control unit 45 predetermined setpoints for the temperature make an adjustment of the throttle 37, whereby a Control of a predetermined temperature value or a Limiting a maximum temperature is possible.
  • the temperature control can also be done with the help of the second Sensor 46 and the control unit 45 depending on predetermined speed setpoint, a speed control of Variable displacement pump 42 are made, wherein the Flow area at the adjustable throttle 37 is changed accordingly. If necessary, both can Control types are combined.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer hydraulischen Steuereinrichtung nach der im Oberbegriff des Patentanspruchs 1 näher angegebenen Gattung.The invention is based on a hydraulic control device according to the specified in the preamble of claim 1 in more detail Genus.

Bei einer aus der WO 01/02736 A1 bekannten hydraulischen LS-Steuereinrichtung geht eine Steuerleitung durch Wegeventile hindurch und führt über Wechselventile zu einer Druckmittelversorgungseinrichtung. Ein 2/2 Wege-Zuschaltventil ist zwischen einen von einer Druckmittelversorgungseinrichtung mit einer Verstellpumpe ausgehenden Zulaufkanal und den der Druckmittelversorgungseinrichtung nähesten Steuerleitungsabschnitt der Steuerleitung und ein Stromregelventil ist zwischen diesen Steuerleitungsabschnitt und einen Rücklaufkanal geschaltet. Das Stromregelventil ist nur für einen kleinen Ölstrom ausgelegt, da nicht nur nach dem Schalten des Zuschaltventils in Durchgangsstellung, sondern auch im normalen Betrieb der Steuereinrichtung dauernd der geregelte Ölstrom, auf den das Stromregelventil eingestellt ist, aus der Steuerleitung in den Rücklaufkanal fließt und der geregelte Ölstrom insofern einen Verluststrom darstellt, der möglichst klein gehalten werden soll. In one known from WO 01/02736 A1 hydraulic LS control device a control line goes through directional control valves through and leads via shuttle valves to a pressure medium supply device. A 2/2 way on-off valve is in between one of a pressure medium supply device with a variable pump outgoing inlet channel and the Pressure medium supply device closest control line section the control line and a flow control valve is between this control line section and a return channel connected. The flow control valve is only for a small Oil flow designed, not only after the switching of the Zuschaltventils in transit position, but also in normal Operation of the control device continuously the regulated oil flow, on which the flow control valve is set, from the control line flows into the return channel and the regulated oil flow insofar represents a leakage current, the smallest possible should be kept.

Die aus der WO 01/02736 A1 bekannte hydraulische Steuereinrichtung kann also nicht dafür verwendet werden, um.ohne Betätigung eines Wegeventils nach dem Schalten des Zuschaltventils eine große hydraulische Leistung zu erbringen. Vielmehr schwenkt die Verstellpumpe nach dem Umschalten des Zuschaltventils auf einen kleinen Förderstrom zurück, sofern kein Wegeventil betätigt ist.The known from WO 01/02736 A1 hydraulic control device so can not be used to, without operation a directional control valve after switching the connecting valve to provide a great hydraulic performance. Much more pivots the variable displacement pump after switching the connecting valve to a small flow back, unless a directional control valve is pressed.

Eine hydraulische Steuereinrichtung mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1 ist aus der DE 195 42 371 A1 bekannt. Bei dieser Steuereinrichtung wird eine Druckwaage in einer Anschlußplatte von einer Konstantpumpe mit Druckmittel versorgt und über einen Steuerkreis mit dem ausgewählten maximalen Lastdruck der gleichzeitig betätigten hydraulischen Verbraucher beaufschlagt, um eine sogenannte LS-Steuerung zu erreichen. Bei vielen Anwendungsfällen wird nun eine zusätzliche Funktion der Arbeitshydraulik gewünscht, welche die hydraulische Leistung eines auf Druck gebrachten und zum Tank geleiteten Volumenstroms nutzt, wobei diese zusätzliche Anwendungsfunktion unabhängig von der Betätigung der Wegeventile in der Regel elektrisch zugeschaltet wird. Solche Anwendungsfälle sind zum Beispiel die Belastung der Arbeitshydraulik in einem Traktor beim Start, um das Öl zu erwärmen, oder eine Bremsfunktion bei einem hydrostatischen Fahrantrieb, wenn zum Beispiel in einem Gabelstapler der.Verbrennungsmotor im Fahrbetrieb bei Gaswegnehmen abgebremst wird. Andererseits soll aber der Regel-Druckabfall am Wegeventil bei betätigtem Ventilschieber so klein wie möglich sein, um Verlustenergie zu vermeiden. Für solche oder ähnliche Zusatzfunktionen weist die vorbekannte Steuereinrichtung an der Endplatte ein elektromagnetisch betätigbares 3/2-Zuschaltventil auf, an dessen drei Anschlüssen ein Zulaufkanal, ein Rücklaufkanal sowie ein Steuerkanal eines Steuerkreises angeschlossen sind. Mit diesem Zuschaltventil in der Endplatte lässt sich die Druckwaage in der Arbeitshydraulik aktivieren, so dass sie einen Druck anstaut, der dem Systemdruck entspricht oder der sich mit Hilfe eines zweiten, nicht dargestellten Vorsteuer-Druckbegrenzungsventils niedriger als der Systemdruck einstellen lässt. Von Nachteil ist nun, dass sich diese Lösung schlecht für eine Steuereinrichtung eignet, bei der anstelle einer Konstantpumpe eine Verstellpumpe zur Druckmittelversorgung verwendet wird. Auch baut diese Lösung mit seinem Zuschaltventil mit drei Anschlüssen relativ aufwendig. Zudem ist diese Bauart wenig variabel und daher schlechter geeignet für besondere Einsatzfälle, wie die proportionale Verstellung in einem Regelkreis.A hydraulic control device with the features of the The preamble of claim 1 is known from DE 195 42 371 A1 known. In this control device is a pressure compensator in a connection plate of a constant pump with pressure medium supplied and via a control circuit with the selected maximum load pressure of the simultaneously actuated hydraulic Consumers charged to a so-called LS control to reach. In many applications now an additional Function of the working hydraulics desired, which the hydraulic Performance of a pressurized and to the tank uses derived volumetric flow, this additional application function regardless of the operation of the directional valves usually switched on electrically. Such use cases are, for example, the load of the working hydraulics in a tractor at take-off to warm up the oil, or a braking function in a hydrostatic drive, if, for example, in a forklift the engine is braked when driving while the throttle is removed. On the other hand, but the rule-pressure drop at the directional control valve when the valve spool is actuated, be as small as possible To avoid loss of energy. For such or similar Additional functions instructs the previously known control device the end plate an electromagnetically actuated 3/2-Zuschaltventil on, at its three terminals one Inlet channel, a return channel and a control channel of a Control circuit are connected. With this connection valve in the end plate can be the pressure compensator in the Activate working hydraulics, giving them a pressure accumulated, which corresponds to the system pressure or with Help of a second, not shown pilot pressure relief valve lower than the system pressure can be set. The disadvantage now is that this Solution is poorly suited for a control device in which Instead of a constant pump, a variable displacement pump for Pressure medium supply is used. Also builds this solution with its three-port on-off valve relative consuming. In addition, this design is not very variable and therefore less suitable for special applications, such as proportional adjustment in a control loop.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße hydraulische Steuereinrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass sie bei einfacherer Bauweise vielseitiger anwendbar ist. Vor allem eignet sie sich für unterschiedliche Druckmittelversorgungseinrichtungen, bei der einmal eine Konstantpumpe mit Druckwaage verwendet werden kann, während im anderen Fall eine Verstellpumpe mit Regler anwendbar ist. Dabei benötigt die Steuereinrichtung relativ wenig zusätzlichen Ventilaufwand, so dass sie kompakt und kostengünstig baut. Durch den speziellen Abgriff des LS-Drucks zwischen Zuschaltventil und Drossel kann der Druckaufbau bei aktiviertem Zuschaltventil bis zum maximalen Systemdruck erfolgen. Die Entlastung der Steuerleitung im LS-Steuerkreis in Ruhestellung wird aufrechterhalten. Ferner ergibt sich der funktionelle Vorteil, dass die Belastung mit Hilfe der Drossel leicht bestimmbar ist.The inventive hydraulic control device with the Characteristic features of claim 1 has the other hand the advantage that they are versatile in simpler construction is applicable. Above all, she is suitable for different pressure medium supply devices, at who once used a constant pump with pressure compensator can be, while in the other case with a variable Regulator is applicable. In this case, the control device requires Relatively little extra valve effort, so they compact and inexpensive builds. Through the special tap the LS pressure between the connection valve and throttle can the Pressure build-up with activated connection valve up to the maximum System pressure done. Relief of the control line in LS control circuit at rest is maintained. Further gives rise to the functional advantage that the load is easily determinable with the help of the throttle.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen hydraulischen Steuereinrichtung möglich. Besonders günstig ist es, wenn gemäß Anspruch. 2 die Drossel verstellbar ausgeführt wird, so dass die Belastung variierbar ist; dadurch eignet sich die Steuereinrichtung besonders für Fälle, in denen unterschiedliche Parameter gesteuert bzw. geregelt werden sollen. Eine besonders zweckmäßige Bauart ergibt sich gemäß Anspruch 3, wenn Zuschaltventil und Drosselstelle in einer Endplatte untergebracht sind. Gemäß den Ansprüchen 4 und 5 kann die Druckmittelversorgungseinrichtung in unterschiedlicher Weise ausgeführt werden, so dass wahlweise Konstantpumpe und Verstellpumpe einsetzbar sind. Weiterhin ergeben sich vorteilhafte Ausgestaltungen gemäß den Ansprüchen 6 und 7, wobei die Belastung der Arbeitshydraulik so gewählt werden kann, dass eine Temperaturbegrenzung im Rücklaufstrom und/oder eine Drehzahlbegrenzung der Pumpe erreichbar sind. Weitere vorteilhafte Ausgestaltungen ergeben sich aus den übrigen Ansprüchen, der Beschreibung sowie der Zeichnung.By the measures listed in the dependent claims are advantageous developments and improvements in the Claim 1 specified hydraulic control device possible. It is particularly favorable, if according to claim. 2 the Throttle is adjustable, so that the load is variable; this makes the control device suitable especially for cases where different parameters be controlled or regulated. A special functional design results according to claim 3, when Sequence valve and throttle point in an end plate are housed. According to claims 4 and 5, the pressure medium supply device in be executed in different ways, so that optional Constant pump and variable pump can be used. Farther result in advantageous embodiments according to the Claims 6 and 7, wherein the load of the working hydraulics can be chosen so that a temperature limit in Return flow and / or a speed limitation of the pump are reachable. Further advantageous embodiments arise from the remaining claims, the description as well as the drawing.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein erstes Ausführungsbeispiel der hydraulischen Steuereinrichtung mit Konstantpumpe in vereinfachter Darstellung und Figur 2 eine zweite Ausführungsform der Steuereinrichtung mit Verstellpumpe in vereinfachter Darstellung.Two embodiments of the invention are in the Drawing shown and in the following description explained in more detail. FIG. 1 shows a first one Embodiment of the hydraulic control device with Constant pump in a simplified representation and Figure 2 a second embodiment of the control device with Variable displacement pump in a simplified representation.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die Figur 1 zeigt eine erste hydraulische Steuereinrichtung 10, bei der mehrere Wegeventile 11, 12, 13, 14 zur Steuerung von nicht näher gezeichneten hydraulischen Verbrauchern vorgesehen sind. Das für eine einfach wirkende Funktion vorgesehene Wegeventil 11 und die für eine doppelt wirkende Funktion vorgesehenen Wegeventile 12 bis 14 sind aneinander geflanscht und zwischen einer Anschlußplatte 15 und einer Endplatte 16 angeordnet, so dass sie einen Wegeventilblock 17 bilden. Der Wegeventilblock 17 wird von einer Konstantpumpe 18 mit Druckmittel versorgt, wobei von einem mit 19 bezeichneten Zulaufanschluß in der Anschlußplatte 15 ein Zulaufkanal 21 ausgeht, der die Anschlußplatte 15 sowie alle Wegeventile 11 bis 14 durchdringt und zur Endplatte 16 führt. An diesen Zulaufkanal 21 sind alle Wegeventile 11 bis 14 parallel angeschlossen. Ferner weist die Anschlußplatte 15 einen Rücklaufanschluß 22 auf, der mit einem alle Wegeventile 11 bis 14 durchdringenden Rücklaufkanal 23 in Verbindung steht und der über eine Rücklaufleitung 24 zu einem Tank 25 entlastet ist.FIG. 1 shows a first hydraulic control device 10, in the multi-way valves 11, 12, 13, 14 for control of unspecified hydraulic consumers are provided. That for a single-acting function provided directional control valve 11 and for a double-acting Function provided directional valves 12 to 14 are connected to each other flanged and between a connection plate 15 and a End plate 16 is arranged so that it has a directional control valve block 17 form. The directional control valve block 17 is of a Constant pump 18 supplied with pressure medium, wherein of a 19 designated inlet connection in the connection plate 15th an inlet channel 21 goes out, the connecting plate 15 and all directional valves 11 to 14 penetrates and the end plate 16 leads. At this inlet channel 21 all valves 11 to 14 connected in parallel. Furthermore, the connection plate 15 to a return port 22, with an all Directional valves 11 to 14 penetrating return channel 23 in Connection stands and the via a return line 24 to a tank 25 is relieved.

In der Anschlußplatte 15 steht der Zulaufanschluß 19 über eine Bypaßleitung 26 mit dem Rücklaufanschluß 22 in Verbindung, wobei in diese Bypaßleitung 26 eine Druckwaage 27 geschaltet ist. Die Druckwaage 27 wird in an sich bekannter Weise auf der einen Seite vom Förderdruck der Konstantpumpe 18 beaufschlagt, während sie auf der anderen Seite von einer Regelfeder 28 und dem Signaldruck aus einem Steuerkreis 29 beaufschlagt wird. Ferner ist in der Anschlußplatte 15 ein Druckbegrenzungsventil 31 vorgesehen, das in den Steuerkreis 29 geschaltet ist und zusammen mit der Druckwaage 27 als vorgesteuertes Druckbegrenzungsventil für den Systemdruck in der ersten Steuereinrichtung '10 dient.In the connection plate 15 is the inlet port 19 via a bypass line 26 with the return port 22 in Connection, wherein in this bypass line 26 a pressure balance 27 is switched. The pressure compensator 27 is in itself known manner on the one hand from the delivery pressure of Constant pump 18 pressurized while on the other Side of a control spring 28 and the signal pressure from a Control circuit 29 is acted upon. Furthermore, in the Connection plate 15, a pressure relief valve 31 is provided, which is connected in the control circuit 29 and together with the pressure compensator 27 as a pilot-operated pressure relief valve for the system pressure in the first controller '10 serves.

Wie die Figur 1 ferner zeigt, sind alle Wegeventile 11 bis 14 in an sich bekannter Weise für eine lastdruckkompensierte Steuerung ausgebildet, die auch als sogenannte LS-Steuerung bezeichnet wird. Zu diesem Zweck sind alle Wegeventile 11 bis 14 an den Steuerkreis 29 angeschlossen, indem von jedem Wegeventil 11 bis 14 eine erste Steuerleitung 32 jeweils über ein Wechselventil 33 an eine'durchgehende zweiten Steuerleitung 34 angeschlossen ist, die einerseits in der Anschlußplatte 15 zur Druckwaage 27 führt und andererseits an die Endplatte 16 angeschlossen ist. Im Steuerkreis 29 ist somit der jeweils maximale Lastdruck von einem der betätigten Wegeventile 11 bis 14 abgreifbar und mit diesem Signaldruck die Druckwaage 27 beaufschlagbar.As FIG. 1 also shows, all directional control valves 11 to 14 in a conventional manner for a load pressure compensated Control is formed, also called LS control referred to as. For this purpose, all valves 11 to 14 connected to the control circuit 29 by each of Directional valve 11 to 14, a first control line 32 respectively via a shuttle valve 33 to a'durchgehend second Control line 34 is connected, on the one hand in the Connection plate 15 leads to the pressure compensator 27 and on the other is connected to the end plate 16. In the control circuit 29 is thus the respective maximum load pressure of one of the operated directional control valves 11 to 14 tapped and with this Signal pressure the pressure compensator 27 acted upon.

Wie die Figur 1 ferner zeigt, ist in der Endplatte 16 ein Querkanal 35 angeordnet, über den der Zulaufkanal 21 vom benachbarten Wegeventil 14 mit dem Rücklaufkanal 23 desselben Wegeventils 14 verbunden ist. In diesen Querkanal 35 sind in Strömungsrichtung gesehen hintereinander ein elektromagnetisch betätigbares Zuschaltventil 36 sowie eine Drossel 37 geschaltet. Das Zuschaltventil 36 ist hier als einfaches 2/2-Ventil ausgeführt. Ferner ist es zweckmäßig, die Drossel 37 verstellbar auszubilden.. Ferner ist die zweite, durchgehende Steuerleitung 34 mit ihrem am weitesten von der Anschlußplatte 15 entfernten,letzten Abschnitt an den Querkanal 35 so angeschlossen, dass sie den Signaldruck zwischen dem Zuschaltventil 36 und der stromabwärts davon liegenden Drossel 37 abgreift. Die beiden Bauelemente Zuschaltventil 36 und verstellbare Drossel 37 liegen somit beide im Arbeitskreis und sind dementsprechend groß ausgelegt. As Figure 1 further shows, in the end plate 16 a Transverse channel 35 is arranged, via which the inlet channel 21 from adjacent directional control valve 14 with the return channel 23rd the same directional valve 14 is connected. In this cross channel 35 are seen in the flow direction one behind the other Electromagnetically actuated Zuschaltventil 36 and a Throttle 37 switched. The Zuschaltventil 36 is here as simple 2/2 valve designed. It is also appropriate the throttle 37 adjustable form .. Furthermore, the second, continuous control line 34 with its farthest from the terminal plate 15, last section to the transverse channel 35 so connected that the signal pressure between the Zuschaltventil 36 and the downstream thereof Throttle 37 picks up. The two components Zuschaltventil 36 and adjustable throttle 37 are thus both in Working group and are designed accordingly large.

Die Konstantpumpe 18 und die Druckwaage 27 bilden hier eine Druckmittelversorgungseinrichtung 38 für die erste Steuereinrichtung 10.The fixed displacement pump 18 and the pressure compensator 27 form one here Pressure medium supply device 38 for the first Control device 10.

Die Wirkungsweise der Steuereinrichtung 10 nach Figur 1 wird wie folgt erläutert, wobei die grundsätzliche Funktion einer lastdruckkompensierten Steuerung als an sich bekannt vorausgesetzt wird.The operation of the control device 10 of Figure 1 is as explained below, the basic function of a load pressure compensated control as known per se is assumed.

Wird von der Steuereinrichtung 10 keine Funktion benötigt, so befinden sich alle Wegeventile 11 bis 14 in ihren gezeichneten Neutralstellungen und auch das nichtbetätigte Zuschaltventil 36 in der Endplatte 16 nimmt seine gezeichnete Sperrstellung ein. In diesem Fall wird der von der Konstantpumpe 18 geförderte Druckmittelstrom von der Druckwaage 27 über die Bypaßleitung 26 unmittelbar zum Tank 25 zurückgeführt. Die Konstantpumpe 18 arbeitet dabei gegen einen relativ niedrigen Umlaufdruck, der von der Regelfeder 28 bestimmt wird. Die im Betrieb anfallenden Drosselquerschnitte der Drossel 37 sind ausreichend groß, so dass die federbeaufschlagte Seite der Druckwaage 27 über den Steuerkreis 29 sicher zum Tank entlastet ist. Die Energieverluste bei diesem Umlaufdruck werden relativ niedrig gehalten.If no function is required by the control device 10, so are all valves 11 to 14 in their drawn neutral positions and also the unactuated Zuschaltventil 36 in the end plate 16 takes its drawn blocking position. In this case, the of the fixed displacement pump 18 funded pressure medium flow of the Pressure compensator 27 via the bypass line 26 directly to the tank 25 returned. The fixed displacement pump 18 works against a relatively low circulation pressure, by the control spring 28 is determined. The incurred during operation Throttle cross sections of the throttle 37 are sufficiently large, so that the spring-loaded side of the pressure compensator 27 on the Control circuit 29 is safely relieved to the tank. The Energy losses at this circulation pressure become relative kept low.

Soll einer oder mehrere der an den Wegeventilen 11 bis 14 angeschlossenen Verbraucher betätigt werden, so wird jeweils der betreffende Steuerschieber in diesem Wegeventil ausgelenkt. Der hierbei auftretende maximale Lastdruck wird über die Wegeventile 11 bis 14 abgegriffen und in dem Steuerkreis 29 ausgewählt, wobei er die Druckwaage 27 beaufschlagt. Der Förderdruck der Konstantpumpe 18 wird dadurch hochgefahren und eine lastdruckkompensierte Steuerung des betätigten Verbrauchers kann in an sich bekannter Weise stattfinden. Das Zuschaltventil 36 in der Endplatte 16 wird dabei nicht betätigt, so dass es den Querkanal 35 in der Endplatte 16 hydraulisch blockiert und somit einen Druckaufbau in dem Zulaufkanal 21 ermöglicht.If one or more of the directional valves 11 to 14 connected consumers are actuated, respectively the relevant spool in this way valve deflected. The occurring maximum load pressure is tapped on the way valves 11 to 14 and in the Control circuit 29 selected, where he the pressure compensator 27th applied. The delivery pressure of the fixed displacement pump 18 is powered up and a load pressure compensated Control of the operated consumer can in itself take place in a known manner. The Zuschaltventil 36 in the End plate 16 is not actuated, so that it is the Cross channel 35 hydraulically blocked in the end plate 16 and thus allowing a pressure build-up in the inlet channel 21.

Soll nun über die geschilderten Funktionen der Steuereinrichtung 10 hinaus eine zusätzliche Funktion der Arbeitshydraulik erwünscht sein, indem die hydraulische Leistung eines auf Druck gebrachten und zum Tank geleiteten Volumenstroms genutzt wird, so kann dies unabhängig von der Betätigungsart der Wegeventile 11 bis 14 mit Hilfe des Zuschaltventils 36 erreicht werden. Eine solche zusätzliche Funktion kann in vielen Fällen erwünscht sein, z.B. wenn durch die Belastung der Arbeitshydraulik in einem Traktor beim Start das Öl erwärmt werden soll. Ein weiterer Anwendungsfall ergibt sich bei einem Gabelstapler mit Verbrennungsmotor und hydrostatischem Fahrantrieb, der im Fahrbetrieb beim Wegnehmen des Gases abgebremst werden soll. In solchen Fällen befinden sich die Wegeventile 11 bis 14 in ihren jeweiligen Mittelstellungen, während das erregte Zuschaltventil 36 seine Offenstellung einnimmt. Der von der Konstantpumpe 18 geförderte Druckmittelstrom kann deshalb über den Zulaufkanal 21 und das geöffnete Zuschaltventil 36, über den Querkanal 35 und die Drossel 37 in den Rücklaufkanal 23 und zum Tank 25 abströmen. Der von der Drossel 37 aufgebaute Staudruck im Querkanal 35 wird über die zweite Steuerleitung 34 abgegriffen und auf die federbeaufschlagte Stirnseite der Druckwaage 27 geführt. Damit ist aber die Druckwaage 27 kurzgeschlossen und die Konstantpumpe 18 kann einen Druck aufbauen, der den am Druckbegrenzungsventil 31 eingestellten Systemdruck erreicht. Mit dem Zuschaltventil 36 wird somit die Druckwaage 27 aktiviert, so dass ein den Umlaufdruck wesentlich übersteigender Druck erreicht wird, der bis zur Höhe des eingestellten Systemdrucks führen kann. Mit Hilfe der Drossel 37 lässt sich dabei der Staudruck im Zulaufkanal einstellen, und somit die Belastung der Arbeitshydraulik. In der Steuereinrichtung 10 kann somit mit Hilfe des Zuschaltventils 36 eine Belastung der Arbeitshydraulik erreicht werden, die als zusätzliche Funktion nutzbar ist.Should now on the described functions of Control device 10 addition to an additional function of Work hydraulics may be desirable by the hydraulic Performance of a pressurized and piped tank Volume flow is used, so this can be independent of the Actuation of the directional valves 11 to 14 with the help of Zuschaltventils 36 can be achieved. Such an extra Function may be desired in many cases, e.g. if by the load of the working hydraulics in a tractor When starting, the oil should be heated. Another Use case results in a forklift with Internal combustion engine and hydrostatic drive in the Driving should be slowed down when removing the gas. In such cases, the directional valves 11 to 14 are in their respective middle positions while that aroused Zuschaltventil 36 assumes its open position. The one of the Constant pump 18 funded pressure medium flow can therefore via the inlet channel 21 and the open connection valve 36, over the transverse channel 35 and the throttle 37 in the Return channel 23 and flow to the tank 25. The one of the Throttle 37 built-up dynamic pressure in the transverse channel 35 is about the second control line 34 tapped and on the spring-loaded end face of the pressure compensator 27 out. But this is the pressure compensator 27 is short-circuited and the Constant pump 18 can build up a pressure on the am Pressure relief valve 31 set system pressure reached. With the Zuschaltventil 36 is thus the Pressure compensator 27 is activated so that the circulation pressure Substantially exceeding pressure is reached, which is up to Level of the set system pressure can lead. With help the throttle 37 can be the back pressure in the inlet channel adjust, and thus the burden of Working hydraulics. In the control device 10 can Thus, with the help of the Zuschaltventils 36 a burden of Working hydraulics can be achieved as additional Function is usable.

Die Figur 2 zeigt in vereinfachter Ausführungsform eine zweite Steuereinrichtung 40, die sich von der ersten Steuereinrichtung 10 nach Figur 1 vor allem durch eine andere, zweite Druckmittelversorgungseinrichtung 41 unterscheidet. Diese zweite Druckmittelversorgungseinrichtung 41 weist eine Verstellpumpe 42 sowie ein zugeordnetes Regelventil 43 auf, wobei zur Begrenzung des Systemdrucks dem Regelventil 43 das Druckbegrenzungsventil 31 zugeordnet ist. In der Anschlußplatte 15 kann daher eine Druckwaage entfallen, während die Endplatte 16 in ihrem Aufbau unverändert bleibt. Anstelle der bisherigen Wegeventile 11 bis 14 sind nur noch drei Wegeventile 11 bis 13 dargestellt.2 shows a simplified embodiment of a second control device 40 extending from the first Control device 10 according to Figure 1, especially by a another, second pressure medium supply device 41 different. This second Pressure medium supply device 41 has a Variable 42 and an associated control valve 43, wherein for limiting the system pressure the control valve 43, the Pressure relief valve 31 is assigned. In the Connection plate 15 can therefore account for a pressure balance, while the end plate 16 remains unchanged in construction. Instead of the previous way valves 11 to 14 are only three-way valves 11 to 13 shown.

Die zweite Steuereinrichtung 40 weist ferner einen ersten Sensor 44 auf, der in dem Rücklaufkanal 23 der Anschlußplatte 15 die Temperatur des abfließenden Druckmittelstromes mißt und der seine Signale an eine elektronische Steuereinheit 45 meldet. Ferner ist in der zweiten Druckmittelversorgungseinrichtung 41 ein zweiter Sensor 46 vorgesehen, der die Drehzahl der Verstellpumpe 42 ermittelt und davon abhängige Signale an die Steuereinheit 45 weitergibt. Ferner ist an der elektronischen Steuereinheit 45 eine erste Sollwerteingabe 47 vorgesehen, mit der eine gewünschte Temperatur des Druckmittelstroms bzw. dessen maximale Temperatur vorgegeben werden kann. An einer zweiten Sollwerteingabe 48 werden Sollwerte für die Drehzahl der Verstellpumpe 42 eingegeben. Die elektronische Steuereinheit 45 ermittelt aus den eingegebenen Soll- und Istwerten eine Regelabweichung und steuert damit eine Stelleinheit 49, mit welcher die verstellbare Drossel 37 in der Endplatte 16 betätigbar ist.The second control device 40 also has a first Sensor 44 which in the return channel 23 of the Connection plate 15 the temperature of the outflowing Pressure medium flow measures and sends its signals to a electronic control unit 45 reports. Furthermore, in the second pressure medium supply device 41 a second Sensor 46 is provided, the speed of the variable 42nd determined and dependent signals to the control unit 45 passes. Furthermore, at the electronic Control unit 45, a first setpoint input 47 is provided, with a desired temperature of the pressure medium flow or whose maximum temperature can be specified. At a second setpoint input 48, setpoints for the Speed of the variable 42 input. The electronic Control unit 45 determined from the entered desired and Actual values are a control deviation and thus controls one Actuator 49, with which the adjustable throttle 37 in the end plate 16 is actuated.

Die Wirkungsweise der zweiten Steuereinrichtung 40 mit der Verstellpumpe 42 zur Druckmittelversorgung entspricht im Wesentlichen derjenigen der ersten Steuereinrichtung 10 nach Figur 1. Darüber hinaus lässt sich mit Hilfe der vom ersten Sensor 44 erfassten Temperatur des abfließenden Druckmittelstroms im Rücklaufkanal 23 und mit den an der Steuereinheit 45 vorgegebenen Sollwerten für die Temperatur eine Verstellung der Drossel 37 vornehmen, wodurch eine Regelung eines vorgegebenen Temperaturwertes bzw. eine Begrenzung einer maximalen Temperatur möglich wird. Anstelle der Temperaturregelung kann auch mit Hilfe des zweiten Sensors 46 und der Steuereinheit 45 abhängig vom vorgegebenen Drehzahl-Sollwert eine Drehzahlregelung der Verstellpumpe 42 vorgenommen werden, wobei der Durchflußquerschnitt an der verstellbaren Drosselstelle 37 entsprechend geändert wird. Bei Bedarf können auch beide Regelungsarten miteinander kombiniert werden.The operation of the second control device 40 with the Variable 42 for pressure medium supply corresponds to Substantially that of the first control device 10 after Figure 1. In addition, with the help of the first Sensor 44 detected temperature of the outflowing Pressure fluid flow in the return channel 23 and with at the Control unit 45 predetermined setpoints for the temperature make an adjustment of the throttle 37, whereby a Control of a predetermined temperature value or a Limiting a maximum temperature is possible. Instead of The temperature control can also be done with the help of the second Sensor 46 and the control unit 45 depending on predetermined speed setpoint, a speed control of Variable displacement pump 42 are made, wherein the Flow area at the adjustable throttle 37 is changed accordingly. If necessary, both can Control types are combined.

Selbstverständlich sind an den gezeigten Ausführungsformen Änderungen möglich, ohne vom Gedanken der Erfindung abzuweichen. So können anstelle der aufgezeigten Parameter Temperatur und Drehzahl auch andere Größen bei Bedarf berücksichtigt werden. Obwohl die Anordnung des Zuschaltventils 36 in der Endplatte 16 besonders vorteilhaft ist, kann dieser Querkanal mit dem eingeschalteten Zuschaltventil und der Drossel auch in der Anschlußplatte angeordnet werden. Weitere Änderungen sind möglich, ohne vom Gedanken der Erfindung abzuweichen.Of course, to the embodiments shown Changes possible without departing from the spirit of the invention departing. So instead of the indicated parameters Temperature and speed also other sizes if necessary be taken into account. Although the arrangement of the Zuschaltventils 36 in the end plate 16 is particularly advantageous is, this cross channel can be switched on with the Sequence valve and the throttle also in the connection plate to be ordered. Further changes are possible without leaving Deviating thoughts of the invention.

Claims (8)

  1. Hydraulic control device, with one or more directional valves (11, 12, 13, 14) which are provided for the control of hydraulic consumers and are connected to an inflow duct (21) and a return duct (23), with a pressure-medium supply device (38, 41), from which pressure medium can be dispensed into the inflow duct (21) and which can be acted upon for a load-pressure-compensated control of the hydraulic consumers, on the one hand, by the conveying pressure of a pump (81, 42) and, on the other hand by a signal pressure picked up at the directional valves (11, 12, 13, 14) and by a regulating spring (28), with a control circuit (29) which is assigned at least one changeover valve (33) and a control line (34) which leads via the existing changeover valves (33) and which transfers the signal pressure forwards to the pressure-medium supply device (38, 41) and has a last control-line portion located downstream of the existing changeover valves (33) and capable of being relieved of pressure to the return duct (23), and with an electromagnetically actuable cut-in valve (36), via which the last control-line portion can be connected to the inflow duct (21) and can be shut off relative to the inflow duct (21), characterized in that the cut-in valve (36) is a two-way/two-position valve, in that the cut-in valve (36) and, downstream of the latter, a throttle (37) are inserted one behind the other between the inflow duct (21) and the return duct (23), and in that the last control-line portion is connected to the connection between the cut-in valve (36) and the throttle (37).
  2. Hydraulic control device according to Claim 1, characterized in that the throttle (37) is designed adjustably.
  3. Hydraulic control device according to Claim 1 or 2, characterized in that the cut-in valve (36) and the throttle (37) are arranged in an end plate (16) to which lead the inflow duct (21), the return duct (23) and the control line (34).
  4. Hydraulic control device according to one of Claims 1 to 3, characterized in that the pressure-medium supply device (38) consists of a fixed-displacement pump (18) and of an assigned pressure balance (27) at which the conveying pressure of the pump (18), the signal pressure from the control circuit (29) and the regulating spring (28) take effect, the pressure balance (27) being arranged particularly in a connection plate (15) built onto a directional valve (11).
  5. Hydraulic control device according to one of Claims 1 to 3, characterized in that the pressure-medium supply device (41) consists of a variable-displacement pump (42) with an assigned regulating valve (43) at which the conveying pressure of the pump (42), the signal pressure from the control circuit (39) and the regulating spring (28) take effect.
  6. Hydraulic control device according to one of Claims 2 to 5, characterized in that a first sensor (44) is provided which detects the temperature of the pressure medium in the return duct (23) and the signals of which are compared with the signals of a temperature desired-value input (47) in an electronic control unit (45), and in that the throttle (37) is adjustable as a function of this with the effect of a reduction of the control deviation.
  7. Hydraulic control device according to one of Claims 2 to 6, characterized in that the variable-displacement pump (42) is assigned a rotational-speed sensor (46), the signals of which are compared with the signals of a rotational-speed desired-value input (48) in an electrical control unit (45), and in that the throttle (37) is adjustable as a function of this with the effect of a reduction of the control deviation.
  8. Hydraulic control device according to one of Claims 1 to 7, characterized in that a plurality of directional valves (11 to 14) for load-sensing control are connected in parallel to the inflow duct (21) and are connected to the control circuit (29).
EP02008997A 2001-04-28 2002-04-23 Hydraulic control circuit Expired - Lifetime EP1253327B1 (en)

Applications Claiming Priority (2)

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DE10120996A DE10120996A1 (en) 2001-04-28 2001-04-28 Hydraulic control device
DE10120996 2001-04-28

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EP1253327B1 true EP1253327B1 (en) 2005-01-12

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GB0303789D0 (en) * 2003-02-19 2003-03-26 Cnh Belgium Nv Apparatus and method for providing hydraulic power to an agricultural implement
JP4062160B2 (en) * 2003-04-23 2008-03-19 コベルコ建機株式会社 Hydraulic valve device
DE10340506B4 (en) 2003-09-03 2006-05-04 Sauer-Danfoss Aps Valve arrangement for controlling a hydraulic drive
DE102004010623A1 (en) * 2004-03-02 2005-09-22 Bosch Rexroth Ag supply system
IT201700023749A1 (en) * 2017-03-02 2018-09-02 Walvoil Spa VALVE DEVICE WITH ACTIVE DISCHARGE IN LOAD SENSING TYPE CIRCUITS

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KR920007650B1 (en) * 1989-02-20 1992-09-14 히다찌 겐끼 가부시기가이샤 Hyydraulic circuit for working machines
DE3905654C2 (en) * 1989-02-24 1998-10-29 Bosch Gmbh Robert Hydraulic control device
DE19930618A1 (en) * 1999-07-02 2001-01-04 Mannesmann Rexroth Ag Hydraulic control arrangement for supplying pressure medium to preferably several hydraulic consumers

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DE50201979D1 (en) 2005-02-17
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