EP2636908A2 - Agencement de commande - Google Patents

Agencement de commande Download PDF

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Publication number
EP2636908A2
EP2636908A2 EP13154142.7A EP13154142A EP2636908A2 EP 2636908 A2 EP2636908 A2 EP 2636908A2 EP 13154142 A EP13154142 A EP 13154142A EP 2636908 A2 EP2636908 A2 EP 2636908A2
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
inlet
consumer
control
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.)
Withdrawn
Application number
EP13154142.7A
Other languages
German (de)
English (en)
Other versions
EP2636908A3 (fr
Inventor
Martin Gustmann
Boris Buchtala
Steffen Rose
Christian Schmidt
Bojan Ferhadbegovic
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2636908A2 publication Critical patent/EP2636908A2/fr
Publication of EP2636908A3 publication Critical patent/EP2636908A3/fr
Withdrawn legal-status Critical Current

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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
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B13/029—Counterbalance 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding 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
    • F15B2211/30—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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves

Definitions

  • the invention relates to a control arrangement according to the preamble of patent claim 1.
  • a primary energy converter such as a diesel engine
  • the pump driven by the diesel engine delivers a pressure fluid flow to a valve block that distributes the oil to the hydraulic consumers.
  • a control arrangement for supplying pressure medium to the consumer is known from EP 2 171 285 B1 known.
  • this control arrangement several consumers are supplied via a control block with pressure medium, wherein in the inlet and in the flow of each consumer, a continuously adjustable orifice, referred to below metering orifice, is arranged. Between the metering orifice and the consumer port, a lowering brake valve is provided in each case, wherein the lowering brake valve located in the inlet releases the pressure medium connection to the consumer and the lowering brake valve located in the drain is acted upon by the pressure in the inlet in the direction of its open position, so that, for example, in pulling load of the pressure medium volume flow in the process can be throttled.
  • the two metering orifices associated with the consumer can be controlled independently of one another, wherein a platform concept can be realized on account of the simple valve designs.
  • load-sensing controls in which the highest load pressure the consumer is reported to a variable displacement pump and this is controlled so that in a pump line is applied to a lying by a predetermined pressure difference across the load pressure pump pressure.
  • the metering orifices of a load-sensing control can be assigned individual pressure compensators, which also maintain a constant pressure difference across the metering orifices of the respective load-pressure-lower hydraulic consumers, so that a load-pressure-independent activation of the respective consumer is made possible.
  • the individual pressure compensators are arranged upstream of the respective metering orifices and throttle the pressure medium volume flow between the pump line and the metering orifices such that the pressure before the metering orifices is independent of the pump pressure only by a specific pressure difference above the individual load pressure lies.
  • the individual pressure compensators are arranged downstream of the metering orifices and throttle between the metering and the consumer the fluid flow so strong that the pressure after all Zumessblenden same, preferably equal to the highest load pressure or slightly above this ,
  • the pump pressure is applied in the same way, so that the pressure difference changes in the same way at all metering orifices, if the pump pressure decreases in the case of an undersupply and the current distribution between the metering orifices is maintained - accordingly, the speed of all consumers is reduced proportionally.
  • Such a circuit is for example in the US 5,878,647 disclosed.
  • each direction of movement of the consumer are respectively assigned to two metering orifices with downstream individual pressure compensator, wherein a metering orifice with assigned individual pressure compensator at a pressure fluid flow to the respective consumer port and the other metering orifice with associated individual pressure compensator from the respective consumer connection flowing pressure medium flow is effective, so that both the inlet volume flow and the drainage volume flow can be adjusted load compensated.
  • Disadvantage of this solution is a considerable device complexity, since each consumer four orifices and four individual pressure compensators are assigned.
  • the present invention seeks to provide a control arrangement that allows the pressure medium supply of multiple consumers with low device complexity.
  • each of a plurality of consumers on the inlet side and the outlet side each associated with a continuously adjustable inlet orifice and a lowering brake valve, the latter allows bypassing the inlet orifice an outflow of pressure fluid from the consumer to a tank.
  • the opening cross section of the lowering brake valve is essentially dependent on the pressure in the inlet, so that when the load is pulled, the pressure medium volume flow in the respective outlet is throttled.
  • at least one individual pressure compensator is assigned to the two metering orifices associated with a load for load-pressure-independent activation of the consumers. In the sense of a LS or LUDV control, the pressure drop across the inlet orifice in the inlet can be controlled via this be kept constant, so that a substantially load pressure independent pressure medium supply of the consumer is ensured.
  • control arrangement is designed as a LS system, wherein the individual pressure compensator is acted upon in the sense of reducing its opening cross-section of the pressure upstream of the associated inlet orifice plate and in the sense of increasing the opening cross section of the load pressure of the respective consumer.
  • control arrangement can also be designed as LUDV system, wherein the individual pressure compensator is then arranged downstream of the associated inlet orifice plate and is acted upon in the opening direction by the pressure downstream of the inlet orifice and in the closing direction of the highest load pressure of the consumer.
  • a check valve is provided which blocks an outflow of the pressure medium from the consumer in the direction of the pressure compensator.
  • An exemplary embodiment of the control arrangement provides for associating an individual pressure compensator with each of two inlet metering orifices assigned to a consumer.
  • the lowering brake valves and also the inlet metering orifice are designed in the manner of a seat valve, wherein both valve types have a blocking position, which lock leakage of pressure medium from the consumer without leaks.
  • a float position valve is provided for setting a floating position, via which an effective in the opening direction control chamber of the respective lowering brake valve with a control pressure, preferably the pump pressure can be acted upon.
  • the lowering brake valves can each be designed with an additive offset so that it only opens when a pressure corresponding to the offset in the sequence is exceeded. In this way, a drain-side clamping of the consumer is guaranteed.
  • a shuttle valve may be provided, the inputs on the one hand in control oil connection with a line leading the inlet pressure and a control chamber of the downstream lowering brake valve and on the other hand in control oil connection with a drain pressure line and a control chamber of standing in the inlet lowering brake valve and whose output is connected to a line carrying the load pressure.
  • the control arrangement according to the invention is preferably designed as a load-sensing control, wherein a pump pressure of a pump is controlled so that it is above the highest load pressure of the consumer by a predetermined pressure difference.
  • This pump can be designed as a variable displacement pump or a constant displacement pump with a bypass valve.
  • control arrangement is designed as a valve block, wherein each consumer is associated with a valve disc with inlet orifices, lowering brake valves and individual pressure compensator.
  • control arrangements explained below are intended to supply hydraulic consumers with a pressure medium volumetric flow which can be switched over and controlled in both directions of consumption.
  • the supply of pressure medium into the inlet of the consumer takes place load-compensated and is thus largely dependent only on the opening cross-section of an inlet orifice plate which will be explained in more detail below.
  • in the embodiments described below in the valve-side return channels of consumers from the inlet pressure unlockable and controllable check valves are provided. Both the inlet valves and the unlocked by the inlet pressure check valves in the return are preferably designed as pilot operated and pressure balanced poppet valves.
  • the control of the inlet and return valves in engagement takes place independently of each other (resolved control edges).
  • This resolved design makes it possible, without the use of additional pressure sensors required in the prior art, to make the return flow rate at pulling loads dependent on the build-up of pressure in the inlet channel.
  • the sink rate can largely be predetermined by the inflow volume flow.
  • the inventive Solution allows the realization of a platform concept in which the essential elements, such as the proportionally controllable inlet valve in seat valve design, the proportionally adjustable shut-off valve in the return channel in seat valve design, various shuttle valves can be used both in control arrangements in LS technology as well as control arrangements in LUDV technology.
  • FIG. 1 shows a highly simplified circuit diagram of a control arrangement according to the invention for supplying pressure to several consumers of a mobile implement, such as an excavator, a backhoe, a mini and compact excavator, a telehandler or the like.
  • the pressure medium supply of the consumer 2 shown here by way of example a differential cylinder, via a control block 4, which has a plurality of valve disks (directional valve sections 4), each of which is associated with one of the consumer 2.
  • Each of the directional control valve sections 4 has two working connections A, B, which can be connected via the valve arrangement described below to connections P, T, T 'and LS of the control block 4.
  • the control arrangement has a pump, in the present case a variable displacement pump 6 whose pressure connection is connected via a pump line 8 to the pressure port P of the control block 4.
  • a variable displacement pump instead of a variable displacement pump, a constant displacement pump with a bypass valve can also be used.
  • the variable displacement pump 6 is designed for example as an axial piston pump whose pivot angle is adjustable via a control cylinder 10.
  • the actuation of the actuating cylinder 10 via a pump control valve 12.
  • the pivot angle is acted upon by a return device 14 in the direction of the maximum pivot angle, while the actuating cylinder 10 can be adjusted to reduce the pivot angle against the force of the return device 14.
  • the pump control valve 12 is by the force of a control spring sixteenth and biased the control pressure in a LS line 18 in the direction of a relief of the actuating cylinder 10, wherein a control oil connection is opened up between an opening in the control room of the actuating cylinder 10 control line 20 to a tank T.
  • LS line 18 is the highest load pressure of the driven consumers, which is tapped at the LS port of the valve block 4.
  • the tank connection T of the valve block 4 is connected via a tank line 22 to the tank T.
  • the pump pressure which is tapped at the pump line 8.
  • This pump pressure is also applied to a pressure port P of the pump control valve 12.
  • the pump volume flow and thus the pump pressure in the pump line 18 increases until at the end faces of the pump control valve 12, an equilibrium of forces from the pressure force of the pump pressure on the one hand and on the other hand from the load pressure of the load pressure diaryen consumer and the force of the control spring 16 sets.
  • the pump pressure is then higher by the given by the spring force pressure difference than the highest load pressure.
  • the basic function of such a pump control is known from the prior art, for example from the aforementioned EP 2 171 285 B1 known, so that further explanations are unnecessary.
  • FIG. 2 shows a first embodiment of a directional control valve section 24 of a valve block 4 according to FIG. 1 ,
  • This directional valve section 24 is designed with consumer connections A, B, a pressure connection P, a tank connection T, an LS connection LS and a further tank connection T ', the latter connections P, T, LS, T' being in pressure medium connection with the adjacent directional control valve sections can.
  • each consumer connection A, B is assigned a metering orifice 26, 28 as well as a respective lowering brake valve 30, 32.
  • at least one individual pressure compensator 34 is provided, via which the pressure drop across the respective inlet orifice 26, 28 can be kept constant.
  • the solution shown is the Directional control valve section 24 designed as LS system, wherein a single individual pressure compensator 34 is associated with the two inlet orifices 26, 28.
  • An input terminal of the spring-biased individual pressure compensator 34 is connected via a pressure channel 36 to the pressure port P of the directional valve section 24.
  • An output of the individual pressure compensator 34 is connected via a branching inlet channel 38 to a respective pressure port P of the two metering orifices 26, 28.
  • the individual pressure compensator 34 is - as explained above - acted upon in the closing direction by the pressure upstream of the inlet orifices 26, 28 and in the opening direction of the individual load pressure of the connected load, which is tapped via an LS channel 40.
  • the output of the shuttle valve 42 is connected to the LS port, so that the respective highest load pressure to the above-described pump control valve or to another connected directional valve section is reported.
  • the two identical feed orifices 26, 28 are each designed as electrically controllable, proportionally adjustable seat valves whose working ports A, B are connected via channels to the working ports A, B.
  • the consumer port A is in the inlet and the consumer port B is in progress.
  • the channel leading to the consumer port A is referred to as the flow channel 44 and the channel leading to the consumer port B is referred to as the return channel 46.
  • the end faces of the two inlet orifices 26, 28 are pressure balanced.
  • the metering orifices 26, 28 can be adjusted from the illustrated blocking position in which an outflow from the consumer in the direction of the pressure compensator 34 is leak-free shut in an opening direction, wherein the opening cross section of the energization of the proportional magnet 48, 50th depends.
  • the pressure downstream of the respective inlet orifice 26, 28 is tapped off at an LS connection of the inlet orifices 26, 28. This pressure is applied to the inputs of another shuttle valve 52 whose output is connected to the aforementioned LS channel 40.
  • the load pressure at the LS connection of the inlet metering orifice 26 is also signaled via a load tap channel 54 to the signal pressure chamber of the lowering brake valve 32 located in the outlet B and thus in the outlet.
  • the load pressure at the connection LS of the other metering orifice 28 is connected via a load tap channel 56 to the signal pressure chamber of the inlet-side lowering brake valve 30.
  • the two signal pressure chambers of the lowering brake valves 30, 32 are separated from each other via the further shuttle valve 52.
  • the two Lastabgriffskanäle 54, 56 are connected via a respective aperture 64, 66 in connection with the tank connection T '.
  • orifices 64, 66 thus serve to relieve pressure in order to avoid an uncontrolled pressure build-up due to leaks in the case of non-actuated valves and thus uncontrolled slide movements of the individual pressure compensator 34 or the lowering brake valves 30, 32 and a resulting uncontrolled operating behavior.
  • the two lowering brake valves 30, 32 are designed as hydraulically pilot-operated seat valves.
  • An input port P of the two lowering brake valves is connected in each case via a channel 58 or 60 to the associated flow channel 44 or the return channel 46.
  • An outlet connection T of the lowering brake valves is in each case via a tank channel 62, 64 in pressure medium connection with the tank connection T of the directional valve section 24.
  • the pressure in the flow channel 44 and in the return channel 46 is limited by designed in the valve seat design pressure relief valves 68, 70.
  • a maximum pressure set to this open a pressure fluid connection to a connected to the tank port T relief channel 67th
  • the load pressure downstream of the inlet orifice 26 is tapped via the Lastabgriffskanal 54 and reported to the signal pressure chamber located in the drain lowering brake valve 32 so that it is controlled in proportion to the inlet pressure and releases a flow cross section.
  • the check valve 32 opens completely under a pressing load.
  • the lowering brake valve 32 is moved to a control position, wherein the flow restricting the cross section established in such a way that the returning volume flow is only so large to adjust on the inlet side a pressure can be approximately the pressure equivalent of the spring force Return spring 74, 76 of the downstream lowering brake valve 32 corresponds. In this way cavitation can be reliably prevented.
  • LS systems are widely used for tractor applications. For some functions, there is a requirement for a floating position in which both sides of the consumer are connected to each other or to the return line. Such a floating position is required, for example, for attachments that are pulled behind the tractor or when leaving rotary consumers.
  • FIG. 3 is a variant of the embodiment according to FIG. 2 represented, wherein a floating position is realized.
  • an electrically switchable float valve 78 is provided, which is designed as a 3/2-way valve, wherein a terminal C is connected via a branching control line 80 to the inputs of two further shuttle valves 82, 84.
  • the float position valve 78 is biased by a spring into a basic position in which the port C is connected to a tank port T, which opens into a tank control line 86.
  • the above-described aperture 66 is arranged.
  • a pressure port P of the float valve 78 is connected via a connecting channel 88 to the pressure channel 36.
  • the two other inputs of the shuttle valves 82, 84 are connected to the load tap channel 54 and 56, respectively.
  • the output of the shuttle valves 82, 84 is then in fluid communication with the two Signal pressure chambers of the lowering brake valves 32 (shuttle valve 82) and 30 (shuttle valve 84).
  • the pressure channel 86 is connected to the inputs of the two shuttle valves 82, 84, so that they are adjusted to a position in which this pump pressure is reported in the signal pressure chambers of the lowering brake valves 30, 32 so that they are completely opened and release an opening cross-section in the valve-internal discharge channel 67 for both consumer sides.
  • the pump pressure is sufficient even with non-actuation of the inlet orifices 26, 28 to open the lowering brake valves 30, 32, as a result of system even when not operating the inlet orifices 26, 28 at least the pressure from the spring preload of the control spring 16 of the pump control valve 12 resulting pressure difference.
  • FIG. 4 shows a directional valve section 24, which is designed as LUDV system.
  • the directional valve section 24 has two inlet orifices 26, 28, which are also again designed as proportionally adjustable, pressure balanced poppet valves and from a spring-biased locking position shown by energization of proportional magnets 48, 50 are adjustable in the direction of an open position.
  • Each inlet orifice 26, 28 is associated with an individual pressure compensator 34 and 90, respectively. Furthermore, two lowering brake valves 30, 32 are provided which can be opened by the pressure in the respective inlet in order to connect the flow channel 44 and the return channel 46 to the tank T. In their basic position are the Lowering brake valves 30, 32 biased into a position in which an outflow from the consumer to the tank T is locked leak-free. The maximum pressure in the channels 44, 46 is again limited by pressure relief valves 68, 70. These are like the inlet orifices 26, 28 and the lowering brake valves 30, 32 formed as seat valves.
  • the inlet of the two pressure compensators 34, 90 is connected in each case via a connecting channel 92 or 94 to the outlet connection A of the inlet measuring orifice 26 or to the outlet connection B of the inlet measuring orifice 28.
  • Their input ports P are connected via the pressure channel 36 to the pressure port P of the directional valve section 24 as in the embodiment described above.
  • the pressure downstream of the respective inlet orifice 26, 28 is applied to the LS connections of the feed orifices 26, 28.
  • This load pressure is reported in an LS reporting line 96 in which a check valve 98 is provided. This opens when the load pressure is greater than the pressure which acts on the LS port of the directional valve section 24.
  • D. h. The greater of these pressures is reported in a branching pressure compensator 100, via which the spring-loaded end faces of the two individual pressure compensators 34, 90 are acted upon by this load pressure.
  • the individual pressure compensators 34, 90 are acted upon in the direction of its closed position by the force of the weak pressure balance spring and the highest load pressure of the consumer.
  • the pressure acts downstream of the respective inlet orifice 26, 28, which is tapped off at the connection channels 92, 94 via a control line 102, 103.
  • the output of the two individual pressure compensators 34, 90 is connected to the flow channel 44 and the return channel 46.
  • a check valve 104, 106 is arranged in each case. These prevent the consumer loads acting directly on the end faces of the lowering brake valves 30, 32.
  • the pressure drop across the inlet-side inlet orifices 26, 28 is kept constant via the individual pressure compensators 34, 90 acted upon in the closing direction by the highest load pressure, the consumer rate of all consumers being proportionally reduced in the event of an undersupply of the consumer.
  • the other functionality corresponds to that of the above-described embodiments.
  • the LS systems open the lowering brake valves 30, 32 at pushing loads completely.
  • When pulling loads adjusts an opening cross-section at the drain-side lowering brake valve 30, 32, so that on the inlet side, a pressure is adjusted, the height of which essentially depends on the biasing force of the return springs 74, 76.
  • FIG. 5 shows a variant of the embodiment according to FIG. 4 , wherein the functionality of the two individual pressure compensators 34, 90 is combined in a pressure compensator unit 112.
  • the basis FIG. 4 explained pressure balance line 100 is connected in this embodiment to an input port LS of the pressure compensator unit 112. This connection is also blocked in the basic position shown.
  • connection channels 92, 94 branch off the two control lines 102, 103, wherein the control line 102 to an effective in adjustment (a) end face and the control line 103 to an effective in the adjustment direction (b) face of the pressure compensator unit 114 leads.
  • a check valve 116, 118 is arranged in each case.
  • the pressure compensator unit 112 further has two control terminals X, Y.
  • the aforementioned end faces of the pressure compensator slide are acted upon by signal lines 120, 122 with the signal pressures at the terminals X, Y.
  • In an adjustment of the pressure compensator slide in the direction (a) or (b) of the LS port of the pressure compensator unit 112 is connected in a corresponding manner with the control port Y or X, so that the respective end face of the pressure compensator slide by the higher of the pressures in the connecting channel 92, 94 or the LS port of the directional valve section 24 is acted upon.
  • current flows through the inlet orifice plate 26 it accordingly releases an opening cross section between the pressure channel 36 and the connection channel 92.
  • connection channel 92 The increasing pressure in the connection channel 92 is then applied to the in FIG. 5 reported left end face of the pressure compensator unit 112 and are, even before the actual pressure compensator shutter comes in control position, a cross section free. About this pre-opened cross section of the pressure from the pressure balance line 100 of the entire system to the opposite end face (right in FIG. 5 ), so that the pressure compensator unit 112 can go to its control position.
  • the lowering brake valve 32 located in the outlet is then in turn completely opened when the load is pressed, so that the pressure medium can flow away from the consumer.
  • the pulling load function corresponds to that of the above-described embodiment.
  • FIG. 6 shows a concrete embodiment of a lowering brake valve, as it is usable in the embodiments described above. It is assumed that it is the lowering brake valve 32 from the previously described embodiments.
  • the other lowering brake valve 30 has a corresponding structure.
  • the illustrated embodiment is designed in cartridge construction, wherein in a valve bore 124, the actual lowering brake valve 32 is inserted.
  • This valve bore 124 is formed in the control block 4 and has two radial ports, into which the load pressure-carrying channel 60 and connected to the tank T relief channel 67 open. In the axial direction, a control port is formed, on which the respective inlet pressure acts, the example in the embodiment according to FIG. 2 tapped by the load pick-off channel 54.
  • the actual lowering brake valve has a main stage with a main piston 130 which is biased by the force of the return spring 76 against a valve seat 132, so that a pressure medium connection from the channel 60 to the discharge channel 67 is shut off. In the opposite direction, the main stage acts as a check valve.
  • the lowering brake valve 32 further has a pilot stage with a pilot piston 134, which is also biased by the return spring 76 against a pilot valve seat 136.
  • the return spring 76 acts on a spring plate 138 on an axial projection of the pilot piston 134 and thus biases both the main piston 130 and the pilot piston 134 in the direction of its closed position.
  • An end face 114 of the axial projection of the pilot piston 134 bears against the control piston 128.
  • the rear of the main piston 130 remote from the valve seat 132 defines a control chamber 142 which is connected via a connecting channel 144 to a space 146, which in turn forms via a shutter forming control notches 148, which in the FIG. 6 designated region are connected to a rear space 150 which is adjacent to the valve seat 136.
  • the in FIG. 6 Located to the left of the pilot valve seat 136 area of a receiving bore for the pilot piston 134 is in fluid communication with the discharge channel 67.
  • the in FIG. 6 right end face of the pilot piston 134 is relieved of pressure to the discharge channel 67.
  • the connection channel 144 is connected to the channel 60 via a nozzle 152.
  • the inlet pressure in the channel 60 acts via the nozzle 152 in the control chamber 142, so that the main piston is tensioned against the force of the return spring 76 against its valve seat 32.
  • About the pressure in the inlet of the control piston 128 is moved to the right and takes the pilot piston 134 against the force of the return spring 76 so that the Pilot piston 134 lifts from the pilot valve seat 136.
  • the diaphragm cross section formed by the fine control notches 148 is opened so that a connection between the connecting channel 144 and the relief channel 67 is established after a predetermined path (additive offset).
  • each consumer port is associated with a metering orifice and a lowering brake valve.
  • At least one inflow-side metering orifice is in operative connection with an individual pressure compensator.
  • each metering orifice is associated with an individual pressure compensator, these can be integrated into a single pressure compensator unit.

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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)
  • Valves And Accessory Devices For Braking Systems (AREA)
EP13154142.7A 2012-03-05 2013-02-06 Agencement de commande Withdrawn EP2636908A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012203386A DE102012203386A1 (de) 2012-03-05 2012-03-05 Steueranordnung

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EP2636908A2 true EP2636908A2 (fr) 2013-09-11
EP2636908A3 EP2636908A3 (fr) 2017-04-26

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CN (1) CN103307048A (fr)
DE (1) DE102012203386A1 (fr)

Cited By (3)

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CH708877A1 (de) * 2013-11-19 2015-05-29 Liebherr Machines Bulle Sa Hydraulikventilanordnung mit Steuerungs-/Regelungsfunktion.
EP3001042A1 (fr) * 2014-09-25 2016-03-30 CNH Industrial Italia S.p.A. Systeme hydraulique
CN108266417A (zh) * 2018-03-04 2018-07-10 太原理工大学 一种高水基高压大流量比例方向阀

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DE102012208944A1 (de) 2012-05-29 2013-12-05 Robert Bosch Gmbh Hydrostatische Ventilanordnung und hydrostatische Steueranordnung mit der Ventilanordnung
CN103629169A (zh) * 2013-11-26 2014-03-12 中国重型机械研究院股份公司 一种锻造操作机钳口夹持液压系统
DE102013224322A1 (de) 2013-11-28 2015-05-28 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102015209325A1 (de) 2015-05-21 2017-01-26 Robert Bosch Gmbh Hydraulische Anordnung zur Regeneration von Druckmittel eines hydraulischen Verbrauchers

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EP3001042A1 (fr) * 2014-09-25 2016-03-30 CNH Industrial Italia S.p.A. Systeme hydraulique
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DE102012203386A1 (de) 2013-09-05
EP2636908A3 (fr) 2017-04-26

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