EP2142808A1 - Hydraulic control arrangement - Google Patents

Hydraulic control arrangement

Info

Publication number
EP2142808A1
EP2142808A1 EP08734422A EP08734422A EP2142808A1 EP 2142808 A1 EP2142808 A1 EP 2142808A1 EP 08734422 A EP08734422 A EP 08734422A EP 08734422 A EP08734422 A EP 08734422A EP 2142808 A1 EP2142808 A1 EP 2142808A1
Authority
EP
European Patent Office
Prior art keywords
pressure
steering
valve
control arrangement
hydraulic 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.)
Granted
Application number
EP08734422A
Other languages
German (de)
French (fr)
Other versions
EP2142808B1 (en
Inventor
Christoph Keyl
Vincenzo Domenico Bollero
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 EP2142808A1 publication Critical patent/EP2142808A1/en
Application granted granted Critical
Publication of EP2142808B1 publication Critical patent/EP2142808B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—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
    • F15B11/003—Systems with 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a hydraulic control arrangement for a mobile work machine with at least two hydraulic consumers, one of which is provided for a lifting function.
  • a forklift usually has a mast along which a fork is movable to raise or lower a load.
  • the mast can also be tilted and moved laterally, these functions are each operated by hydraulic cylinders.
  • proportional valves are provided in the known solution, via which the pressure medium volume flow to the respective hydraulic cylinder can be adjusted.
  • the pressure medium supply usually takes place via an LS variable displacement pump or a fixed displacement pump with bypass pressure compensator. Depending on the highest load pressure of all consumers, the variable displacement pump or the bypass pressure compensator can be controlled such that the pump pressure is above the highest load pressure by a predetermined ⁇ p.
  • a problem may occur when, for example, raised the empty, unloaded fork and at the same time the mast tilt is to be changed.
  • the load pressure at the tilting cylinder in this case is greater than the load pressure of the lifting cylinder, so that the latter is preferably supplied with pressure medium and the fork is raised relatively quickly, while the tilting movement is very slow or even stopped. This problem occurs in virtually all conventional forklifts.
  • the object of the invention is to provide a hydraulic control arrangement for a mobile work machine in which several consumers can be controlled simultaneously.
  • the at least two consumers of the mobile working machine are supplied with pressure medium via a pump as a function of the highest load pressure.
  • the pressure medium volume flow to an effective in the direction of lifting the consumer and the pressure medium flow to another consumer are each controlled by a LUDV valve with a Zulaufmessblende and a downstream pressure compensator in the closing direction of a pressure corresponding to about the highest load pressure of the consumer and in the opening direction downstream of the inlet orifice is acted upon.
  • LUDV controls load pressure-independent flow distribution
  • LUDV pressure compensators throttle the pressure medium flow rate so strong that the pressure after all Zumessblenden same, preferably equal to the highest load pressure or slightly above this. When undersatured, the pressure downstream of the metering orifice does not change.
  • the pump pressure is applied in the same way, so that the pressure difference at all metering orifices changes in the same way if the pump pressure becomes lower during undersaturation - thus ensuring a proportional flow distribution of the delivery rate to the consumers, so that, for example, an unloaded fork lifted a fork lift and at the same time a mast of the forklift can be tilted.
  • a LUDV valve with a metering orifice and a LUDV pressure compensator two consumers are assigned, which are provided, for example, for tilting and moving a mast of a forklift.
  • the pressure medium flow direction to and from the consumer is then controlled via a respective directional control valve.
  • a respective directional control valve D. h.,
  • the metering orifices of the LUDV valves are very simple, designed to be continuously adjustable in one direction, so that the circuit can be implemented very inexpensively.
  • the pressure compensator of the common LUDV valve can be assigned a pressure reducing valve.
  • the hydraulic actuation of a steering of the mobile work machine is preferably carried out via an LS valve with an inlet orifice and a steering pressure compensator.
  • the steering pressure compensator in the closing direction is acted upon by the pressure in front of the associated inlet orifice and in the opening direction by a spring and the pressure in a control line.
  • This control line is connected to a line section leading the load pressure of the steering.
  • a line section located downstream of the steering pressure scale prefferably to be connected via a control channel and a check valve closing in the direction of the steering to a LS line leading to the highest load pressure of the loads.
  • control line (118) leads from a pressure medium flow path upstream of the steering pressure balance (112) to a line section carrying the load pressure of the steering, wherein two nozzles (120, 122) are arranged in the control line (118) and in the area between the two two nozzles (120, 122) branches off to an effective in the opening direction of the steering pressure balance (112) control chamber control channel (124) which is connected via a check valve (126) with a highest load pressure leading LS line (60).
  • the control arrangement can be implemented particularly easily if the pump for supplying pressure medium is a constant-displacement pump to which a bypass pressure compensator is assigned, which is acted upon in the opening direction by the pump pressure and in the closing direction by the highest load pressure of the consumers.
  • the LS line can be connected to a pressure relief valve via a relief valve with a tank.
  • This relief valve is designed as a flow control valve.
  • the control arrangement according to the invention is preferably used for controlling a forklift, wherein a LUDV valve for controlling the lifting function and a LUDV valve for controlling the tilting and the lateral displacement of a mast of the fork-lift truck are provided.
  • Figure 1 is a circuit diagram of a control arrangement of a forklift truck with a lift, a tilt and a shift function
  • Figure 2 is a detail of the control arrangement of Figure 1;
  • Figure 3 shows the control arrangement of Figure 1 with integrated LS steering and
  • FIG. 4 shows a variant of the circuit according to FIG. 3.
  • FIG. 1 shows a circuit diagram of a hydraulic control arrangement of a fork-lift truck.
  • This control arrangement is formed for example by a mobile control block 1, which consists essentially of a LUDV section 2, two-way valve sections 4, 6 and an end plate 8.
  • the mobile control block 1 has a pressure port P, a tank port T and a working port A at the LUDV section 2 and each working ports A, B at the two-way valve sections 4, 6.
  • the illustrated mobile control block 1 is for driving a mast and the fork of the forklift provided, via a lifting cylinder 10, the fork can be raised or lowered.
  • a tilting cylinder 12 is provided for tilting the fork leading the fork and a displacement cylinder 14 for laterally displacing the mast.
  • the lifting cylinder 10 is a differential cylinder, wherein a bottom-side cylinder chamber 16 is connected via a working line 18 to the working port A of the LUDV section 2.
  • the tilting cylinder 12 is designed as a double cylinder with two parallel-connected differential cylinders, wherein the bottom-side cylinder chambers are connected via a consumer line 20 and the two piston rod-side annular spaces via a further consumer line 22 to the working ports B and A of the directional valve section 4.
  • a lowering brake valve 24 is arranged, which allows a pressure medium supply from the working port A to the two annular spaces unhindered and throttles the return of the two annular spaces to the working port A, so that a controlled tilting of the mast is made possible.
  • Such lowering brake valves or counter-balance valves are known from the prior art, so that further explanations are unnecessary.
  • the displacement cylinder 14 is designed as a synchronous cylinder, wherein the two annular spaces are connected via a working line 26 and a further working line 28 to the working ports A, B of the directional valve section 6.
  • a 4/3-way switching valve 34 and 32 is respectively provided, which are biased in the blocking position shown and over - as will be explained in more detail - the pressure fluid flow direction to and from the cylinders 12, 14 adjustable is.
  • the LUDV section 2 has a LUDV valve 34 which is assigned to the two cylinders 12, 14 and which consists of a metering orifice 36 and a LUDV pressure compensator 38 connected downstream thereof.
  • the LUDV pressure compensator 38 is acted upon in the direction of its closed position by the highest load pressure or a pressure approximately corresponding thereto and in the opening direction by the pressure downstream of the respective upstream metering orifice 36.
  • the metering orifice 36 is designed by a continuously adjustable 2/2-way valve, which is biased in its closed position shown.
  • the metering orifice can be opened by energizing a proportional magnet 40 for adjusting the pressure medium volume flow to the consumers 12, 14.
  • the pressure medium volume flow to the lifting cylinder 10 is also set via a LUDV valve, which is referred to below as lifting LUDV valve 42.
  • lifting LUDV valve 42 Its basic structure corresponds to that of the LUDV valve 34 - it thus essentially consists of a lifting metering orifice 44 and one of these downstream lifting LUDV pressure compensator 46.
  • the lifting metering orifice 44 is also designed by a continuously adjustable 2/2-way valve, whose opening cross-section is in turn adjustable via a proportional magnet 48.
  • the lifting of a load by supplying pressure medium in the bottom-side cylinder chamber 16 of the lifting cylinder 10.
  • a LS-valve 50 Such a LS-valve consists essentially of a continuously adjustable LS metering orifice 52, which is associated with a LS-pressure compensator 54. This is in the illustrated embodiment, the LS metering orifice 52 upstream and applied in the direction of its closed position by the force of a spring and the pressure after the LS metering orifice and in the opening direction of the pressure upstream of the LS metering orifice 52.
  • the LS metering orifice 52 is designed as a 2/2-way seat valve, which allows a leak-free shut-off of the working line 18 in its illustrated blocking position.
  • the LS metering orifice 52 can be adjusted by means of a proportional solenoid 56 or by hand. Further details of the described LS / LUDV valves are explained with reference to FIG.
  • the pressure port P of the mobile control block 1 is designed to the output port of a LS pump, which may be formed for example as a fixed displacement pump.
  • the flow of this constant pump, not shown, is then adjusted via a bypass pressure compensator 58, which is acted upon in the opening direction by the pump pressure and in the closing direction of the highest load pressure of all consumers and by the force of a pressure compensator spring.
  • the pump pressure is always adjusted by a force corresponding to the spring corresponding pump ⁇ above the highest load pressure, which is tapped in an LS line 60.
  • this is connected via a designed as a flow control valve relief valve 62 connected to the tank port T of the mobile control block 1 drain line 64.
  • a LS pressure relief valve 66 is provided to protect the pressure in the LS line 60. Further details of the LUDV section 2 will be explained with reference to the enlarged view in FIG.
  • the pressure medium flows from the pressure port P via an inlet channel 68 to the input port of the lifting metering orifice 44 and the LUDV metering orifice 36.
  • the output port of the LUDV metering orifice 36 is connected via a pressure compensator channel 70 to the input port of the LUDV pressure compensator 38, so that these in Opening direction of the pressure downstream of the LUDV metering orifice 36 is acted upon.
  • this opening cross section is set via the proportional magnet 40.
  • a rear control chamber 72 of the LUDV pressure compensator 38 is connected to the LS line 60, so that acts on the back of the pressure compensator piston, the pressure in the LS line 60 in the closing direction. Since the highest load pressure of all consumers or at least a corresponding pressure is present in this, the highest load pressure also arises at the entrance of the LUDV pressure compensator 38 in the control position. This highest load pressure is throttled over the LUDV pressure compensator 38 to the actual load pressure of the associated consumer and guided via the connected to the output terminal of the LUDV pressure compensator 38 feed line 74 to the associated consumer. In the flow line 74 a in the direction of the two cylinders 12, 14 opening check valve 76 is arranged, so that a pressure medium backflow to the LUDV valve 34 is prevented. The displaced from the cylinders 12, 14 pressure fluid flows through the drain passage 64 and the tank port T to the tank down.
  • the lift-LUDV valve 42 has in principle the same structure as the LUDV valve 34.
  • the input of the lifting metering orifice 44 is connected to the inlet channel 68 and the output via a further pressure compensator channel 74 to the input of the lifting LUDV pressure compensator 46 connected.
  • Their rear control chamber 76 is also connected to the LS line 60, so that the pressure compensator piston of the lifting LUDV pressure compensator 46 is acted upon in the closing direction by the highest load pressure and in the opening direction by the pressure downstream of the lifting metering orifice 44. The adjustment of this lifting metering orifice 44 takes place via the proportional magnet 48.
  • the output connection of the lifting LUDV pressure compensator 46 is connected to the working connection A via a feed channel 82 and a check valve 84 which opens in the direction of the working connection A.
  • a feed channel 82 In the area between the Working port A and the check valve 84 branches from the feed channel 82 from a return channel 86, in which the effective in the lowering direction LS-valve 50 is arranged.
  • the input of the LS inlet orifice 52 is connected to the return channel 86.
  • the output is connected via a pressure compensator channel 88 to the input of the LS-pressure compensator 54.
  • Their pressure compensator piston is acted upon in the closing direction by the force of a spring 90 and the pressure at the outlet of the LS inlet orifice 52.
  • This control pressure is tapped via a control channel 92 in the pressure compensator channel 88. In the opening direction, the pressure acts upstream of the LS Zulaufmessblende 52.
  • This pressure is tapped via a control channel 94, wherein a part of the control oil flow path, indicated in Figure 2 with 94a, is integrated into the LS metering orifice 52.
  • the adjustment of the opening cross section of the LS metering orifice 52 takes place via the proportional magnet 56 or manually via a handle 96.
  • the LS-valve 50 running off the lifting cylinder 10 pressure medium flow rate is held constant load pressure independent.
  • the LS metering orifice 52 is designed as a seat valve, so that in the illustrated closed position a leakage-free support of the lifting cylinder 10 takes place.
  • the LS Zumeßblende 52 is opened, the lowering speed can be kept constant load pressure, as in the control position of the LS pressure compensator 54 a constant, the force of the spring 90 corresponding pressure difference across the LS Zulaufmessblende 52 is adjusted.
  • the bypass pressure compensator 58 is, as already mentioned, acted upon by the force of a pressure compensator spring 98 and the pressure in the LS line in the closing direction and in the opening direction by the pressure in the inlet channel 68, which is tapped off via a channel 100.
  • the relief valve 62 and the LS pressure relief valve 66 each extend between the LS line 60 and the drain channel 64.
  • the two cylinders 12, 14 are connected in parallel, it being provided that only one of the two consumers is switched on.
  • the two cylinders 12, 14 upstream directional control valves 30, 32 are each designed as 4/3-way valves and biased by a centering spring assembly in its illustrated basic position.
  • the adjustment in the switching positions a, b via switching magnets.
  • switching the Wegevntils 30 in the switching position a of the flow channel 74 is connected to the working port A and the drain line 64 to the working port B.
  • the two tilting cylinders 12 are extended and the mast tilt is correspondingly reduced.
  • switching the directional control valve 32 in the switching position a is then moved according to the displacement cylinder 14 as shown in Figure 1 to the right.
  • the two working ports A, B of the cylinder 12 are connected to the flow channel 64 and the feed channel 74 so that, for example, the mast is tilted over the tilting cylinder 12, wherein the tilting speed over that in the return located lowering brake valve 24 is determined.
  • FIG. 3 shows an exemplary embodiment in which a steering system 102 is integrated into the circuit according to FIGS. 1 and 2.
  • a steering system 102 is integrated into the circuit according to FIGS. 1 and 2.
  • Such steering usually has a steering cylinder 104 which is supplied for steering via a steering unit 106 with pressure medium.
  • Such steering units 106 also called Orbitrol, are described for example in the data sheet RD 14 365 Bosch Rexroth AG.
  • the steering unit 106 consists essentially of a metering pump and a hand-operated servo valve in rotary valve construction. The size of the metering pump is chosen so that with three to five steering wheel turns from the stop to the stop of the steering can be steered. About the servo valve while a metering orifice is set.
  • the pressure medium supply of the steering unit 106 via a branched off from the inlet channel 68 steering line 108 which is connected via a steering port C and a working line 110 to the steering unit 106.
  • a steering pressure compensator 112 is arranged, which forms an LS valve together with the integrated into the steering unit 106 metering orifice, via which the pressure medium flow rate for adjusting the steering cylinder 104 can be kept constant independent of load.
  • the steering pressure gauge 112 is in the closing direction from the upstream pressure, i. acted upon by the pressure in the region of the terminal C.
  • This control pressure is tapped via a steering control line 114.
  • an adjustable pressure compensator spring 116 and a steering control pressure, which is tapped on a control line 118.
  • This extends from the steering unit 106 to an upstream of the steering pressure balance 112 located portion of the steering line 108.
  • the load pressure of the steering can be tapped.
  • two nozzles 120, 122 are arranged in the control line 118, which together form a pressure divider.
  • control channel 124 In the area between the two nozzles 120, 122 branches off a control channel 124 which is also connected to a spring-side control chamber of the steering pressure balance 112, so that the pressure in the control channel 124 acts in the opening direction on the piston of the steering pressure balance 112.
  • control channel 124 is connected via a further check valve 126 to the LS line 60.
  • a predetermined pressure can then be set in the area between the nozzles 120, 122, which is a certain pressure difference above the steering load pressure.
  • the steering 102 is supplied with pressure medium, wherein above the two orifices 36 and 44 of the LUDV consumers 10, 12, 14 no ⁇ is present, since with a suitable choice of the nozzle 120 at the entrance of associated LUDV pressure compensator 38, 46, the same pressure as in the control channel 124 is adjusted and this pressure with a suitable nozzle selection (nozzle 120) corresponds to the pump pressure, so that no Pressure medium or only a small volume flow to the other LUDV consumers flows, but the steering remains fully functional.
  • a pressure reducing valve 128 is provided, via which in the directional control valve sections 4, 6, a lower working pressure than in the LUDV section 2 can be set.
  • the pressure reducing valve 128 is preferably arranged in the region between the LUDV pressure compensator 38 and the check valve 76.
  • FIG. 4 shows a further possibility of integrating the steering system 102 into the circuit according to FIG. 1, wherein the differences between the exemplary embodiments in FIGS. 3 and 4 lie merely in the tapping of the load pressure acting on the steering pressure compensator 112.
  • the load pressure of the steering unit 106 is tapped via a channel 130, which has no connection to the steering line 108 in contrast to the control line 118 from the above-described embodiment.
  • the control channel 124 connects in this embodiment, the LS line 60 to the working line 110, so that the pressure downstream of the steering pressure gauge 112 is reported via the check valve 126 in the LS line 60.
  • This pressure is higher than the load pressure of the steering.
  • the pressure balance spring 116 and the pressure in the channel 130 act on the steering pressure balance 112 in the opening direction. This pressure corresponds approximately to the load pressure of the steering (pressure downstream of the steering metering orifice).
  • the pressure in the inlet channel 68 decreases and the respective load pressure of the LUDV consumers is applied to the outlet metering orifice via the LUDV pressure compensators, so that the pressure difference correspondingly exceeds the LUDV orifices fall and less pressure fluid flows to the LUDV consumers or these are no longer supplied with pressure medium.
  • the steering unit 106 is supplied with pressure medium fully open steering pressure balance 112, so that the steering can still be operated.
  • Such integration of a steering in a LUDV control arrangement is known per se from DE 101 19 276 A1, so that further embodiments are unnecessary. In principle, the above-described control arrangements can also be applied to other mobile machines, such as wheel loaders, mini excavators, etc.
  • a hydraulic control arrangement for a mobile work machine in particular for a forklift, with at least two hydraulic consumers, one of which has a lifting function.
  • the two consumers are each controlled via a LUDV valve with inlet orifice plate and downstream LUDV pressure compensator.
  • Control channel further check valve

Abstract

The invention relates to a hydraulic control arrangement for a mobile machine tool, particularly for a forklift, comprising at least two hydraulic loads (10, 12), one of them having a lifting function. According to the invention, the two loads are each controlled via a LUDV valve with inflow measuring diaphragm (36, 44) and LUDV pressure regulator (46) connected downstream.

Description

Beschreibung description
Hydraulische SteueranordnungHydraulic control arrangement
Die Erfindung betrifft eine hydraulische Steueranordnung für eine mobile Arbeitsmaschine mit zumindest zwei hydraulischen Verbrauchern, von denen einer für eine Hebefunktion vorgesehen ist.The invention relates to a hydraulic control arrangement for a mobile work machine with at least two hydraulic consumers, one of which is provided for a lifting function.
In der US 6,293,099 B1 ist eine derartige Steueranordnung beschrieben, die zur Ansteuerung der Verbraucher eines Gabelstaplers vorgesehen ist. Ein Gabelstapler hat üblicherweise einen Mast, entlang dem eine Gabel verfahrbar ist, um eine Last anzuheben oder abzusenken. Der Mast lässt sich des Weiteren neigen und seitlich verschieben, wobei diese Funktionen jeweils über Hydraulikzylinder betätigt werden. Zur Steuerung des Druckmittelvolumenstroms zum jeweiligen Hydraulikzylinder sind bei der bekannten Lösung Proportionalventile vorgesehen, über die der Druckmittelvolumenstrom zum jeweiligen Hydrozylinder eingestellt werden kann. Die Druckmittelversorgung erfolgt üblicherweise über eine LS-Verstellpumpe oder eine Konstantpumpe mit Bypassdruckwaage. Die Verstellpumpe oder die Bypassdruckwaage ist in Abhängigkeit vom höchsten Lastdruck aller Verbraucher so ansteuerbar, dass der Pumpendruck um ein vorbestimmtes Δp oberhalb des höchsten Lastdrucks liegt.Such a control arrangement is described in US Pat. No. 6,293,099 B1, which is provided for controlling the consumers of a forklift truck. A forklift usually has a mast along which a fork is movable to raise or lower a load. The mast can also be tilted and moved laterally, these functions are each operated by hydraulic cylinders. For controlling the pressure medium volume flow to the respective hydraulic cylinder proportional valves are provided in the known solution, via which the pressure medium volume flow to the respective hydraulic cylinder can be adjusted. The pressure medium supply usually takes place via an LS variable displacement pump or a fixed displacement pump with bypass pressure compensator. Depending on the highest load pressure of all consumers, the variable displacement pump or the bypass pressure compensator can be controlled such that the pump pressure is above the highest load pressure by a predetermined Δp.
Bei derartigen Steueranordnungen kann beispielsweise ein Problem auftreten, wenn beispielsweise die leere, unbelastete Gabel angehoben und gleichzeitig die Mastneigung verändert werden soll. Der Lastdruck am Neigezylinder ist in diesem Fall größer als der Lastdruck des Hebezylinders, so dass letzterer bevorzugt mit Druckmittel versorgt wird und die Gabel vergleichsweise schnell angehoben wird, während die Neigebewegung sehr langsam erfolgt oder sogar abgestoppt wird. Dieses Problem tritt praktisch bei allen herkömmlichen Gabelstaplern auf.In such control arrangements, for example, a problem may occur when, for example, raised the empty, unloaded fork and at the same time the mast tilt is to be changed. The load pressure at the tilting cylinder in this case is greater than the load pressure of the lifting cylinder, so that the latter is preferably supplied with pressure medium and the fork is raised relatively quickly, while the tilting movement is very slow or even stopped. This problem occurs in virtually all conventional forklifts.
Man könnte nun versuchen, im Druckmittelströmungspfad zu dem Neigezylinder ein LS-Ventil mit einer Zumessblende und einer Druckwaage anzuordnen, die vom Druck vor und nach der Zumessblende beaufschlagt ist. In diesem Fall könnten das Anheben der Gabel und das Neigen des Mastes gleichzeitig erfolgen, solange der maximal mögliche Pumpenförderstrom nicht überschritten wird. Im Falle einer Unter- Versorgung d. h., in dem Fall, in dem die Pumpe nicht genügend Druckmittel fördern kann, wird der lastdruckhöhere Verbraucher wieder langsamer, weil der vor dessen Zumessblende anstehende Pumpendruck abfällt und damit die Druckdifferenz über diese Zumessblende wieder kleiner wird - es stellt sich die gleiche Problematik wie bei der eingangs genannten Steueranordnung mit Proportionalventilen ein.One could now try to arrange in the pressure medium flow path to the tilting cylinder LS valve with a metering orifice and a pressure balance, which is acted upon by the pressure before and after the metering orifice. In this case, raising the fork and tilting the mast could be done simultaneously as long as the maximum possible pump flow rate is not exceeded. In the case of a Supply ie, in the case in which the pump can not deliver enough pressure medium, the load pressure higher consumer is slower again, because the pending before the metering orifice pump pressure drops and thus the pressure difference across this metering orifice is smaller again - it poses the same problem in the aforementioned control arrangement with proportional valves.
Dem gegenüber liegt der Erfindung die Aufgabe zugrunde, eine hydraulische Steueranordnung für eine mobile Arbeitsmaschine zu schaffen, bei der mehrere Verbraucher gleichzeitig ansteuerbar sind.On the other hand, the object of the invention is to provide a hydraulic control arrangement for a mobile work machine in which several consumers can be controlled simultaneously.
Diese Aufgabe wird durch eine hydraulische Steueranordnung für eine mobile Arbeitsmaschine mit den Merkmalen des Patentanspruchs 1 gelöst.This object is achieved by a hydraulic control arrangement for a mobile work machine having the features of patent claim 1.
Erfindungsgemäß werden die zumindest zwei Verbraucher der mobilen Arbeitsmaschine über eine Pumpe in Abhängigkeit vom höchsten Lastdruck mit Druckmittel versorgt. Der Druckmittelvolumenstrom zu einem in Richtung Heben wirksamen Verbraucher und der Druckmittelvolumenstrom zu einem weiteren Verbraucher werden jeweils über ein LUDV-Ventil mit einer Zulaufmessblende und einer nachgeschalteten Druckwaage gesteuert, die in Schließrichtung von einem etwa den höchsten Lastdruck der Verbraucher entsprechenden Druck und in Öffnungsrichtung vom Druck stromabwärts der Zulaufmessblende beaufschlagt ist.According to the invention, the at least two consumers of the mobile working machine are supplied with pressure medium via a pump as a function of the highest load pressure. The pressure medium volume flow to an effective in the direction of lifting the consumer and the pressure medium flow to another consumer are each controlled by a LUDV valve with a Zulaufmessblende and a downstream pressure compensator in the closing direction of a pressure corresponding to about the highest load pressure of the consumer and in the opening direction downstream of the inlet orifice is acted upon.
Bei derartigen LUDV-Steuerungen (lastdruckunabhängige Durchflussverteilung) drosseln die stromab der Zumessblende angeordneten LUDV-Druckwaagen den Druckmittelvolumenstrom so stark an, dass der Druck nach allen Zumessblenden gleich, vorzugsweise gleich dem höchsten Lastdruck ist oder leicht über diesem liegt. Bei einer Untersättigung ändert sich der Druck stromabwärts der Zumessblende nicht. Vor allen Zumessblenden steht in gleicher Weise der Pumpendruck an, so dass sich an allen Zumessblenden die Druckdifferenz in gleicherweise ändert, wenn bei Untersättigung der Pumpendruck geringer wird - damit ist eine proportionale Durchflussverteilung der Fördermenge zu den Verbrauchern gewährleistet, so dass beispielsweise auch eine unbelastete Gabel eines Gabelstaplers angehoben und gleichzeitig ein Mast des Gabelstaplers geneigt werden kann.In such LUDV controls (load pressure-independent flow distribution) arranged downstream of the metering orifice LUDV pressure compensators throttle the pressure medium flow rate so strong that the pressure after all Zumessblenden same, preferably equal to the highest load pressure or slightly above this. When undersatured, the pressure downstream of the metering orifice does not change. In front of all metering orifices, the pump pressure is applied in the same way, so that the pressure difference at all metering orifices changes in the same way if the pump pressure becomes lower during undersaturation - thus ensuring a proportional flow distribution of the delivery rate to the consumers, so that, for example, an unloaded fork lifted a fork lift and at the same time a mast of the forklift can be tilted.
Bei einer einfach aufgebauten Lösung kann es ausreichen, wenn ein weiterer Verbraucher über ein Proportionalventil angesteuert ist. Bei einem besonders einfach aufgebauten Ausführungsbeispiel werden einem LUDV-Ventil mit einer Zumessblende und einer LUDV-Druckwaage zwei Verbraucher zugeordnet, die beispielsweise zum Neigen und zum Verschieben eines Masts eines Gabelstaplers vorgesehen sind.In a simply constructed solution, it may be sufficient if another consumer is controlled via a proportional valve. In a particularly simple embodiment, a LUDV valve with a metering orifice and a LUDV pressure compensator two consumers are assigned, which are provided, for example, for tilting and moving a mast of a forklift.
Die Druckmittelströmungsrichtung zum und vom Verbraucher wird dann über jeweils ein Wegeventil gesteuert. D. h., bei dieser Lösung sind die Zumessblenden der LUDV-Ventile sehr einfach, in einer Richtung stetig verstellbar ausgeführt, so dass sich die Schaltung sehr preisgünstig realisieren lässt.The pressure medium flow direction to and from the consumer is then controlled via a respective directional control valve. D. h., In this solution, the metering orifices of the LUDV valves are very simple, designed to be continuously adjustable in one direction, so that the circuit can be implemented very inexpensively.
In dem Fall, in dem der Arbeitsdruck der über ein gemeinsames LUDV-Ventil angesteuerten Verbraucher geringer als der Arbeitsdruck der anderen Verbraucher ist, kann der Druckwaage des gemeinsamen LUDV-Ventils ein Druckreduzierventil zugeordnet sein.In the case in which the working pressure of the consumers controlled via a common LUDV valve is less than the working pressure of the other consumers, the pressure compensator of the common LUDV valve can be assigned a pressure reducing valve.
Die hydraulische Betätigung einer Lenkung der mobilen Arbeitsmaschine erfolgt vorzugsweise über ein LS-Ventil mit einer Zulaufmessblende und einer Lenkungsdruckwaage.The hydraulic actuation of a steering of the mobile work machine is preferably carried out via an LS valve with an inlet orifice and a steering pressure compensator.
Bei einer Variante ist die Lenkungsdruckwaage in Schließrichtung vom Druck vor der zugeordneten Zulaufmessblende und in Öffnungsrichtung von einer Feder und dem Druck in einer Steuerleitung beaufschlagt ist. Diese Steuerleitung ist mit einem den Lastdruck der Lenkung führenden Leitungsabschnitt verbunden.In one variant, the steering pressure compensator in the closing direction is acted upon by the pressure in front of the associated inlet orifice and in the opening direction by a spring and the pressure in a control line. This control line is connected to a line section leading the load pressure of the steering.
Dabei wird es bevorzugt, wenn ein stromabwärts der Lenkungsdruckwaage gelegener Leitungsabschnitt über einen Steuerkanal und ein in Richtung zur Lenkung schließendes Rückschlagventil mit einer den höchsten Lastdruck der Verbraucher führenden LS-Leitung verbunden ist.In this case, it is preferable for a line section located downstream of the steering pressure scale to be connected via a control channel and a check valve closing in the direction of the steering to a LS line leading to the highest load pressure of the loads.
Bei einer alternativen Lösung führt die Steuerleitung (118) von einem Druckmittelströmungspfad stromaufwärts der Lenkungsdruckwaage (112) zu einem den Lastdruck der Lenkung führenden Leitungsabschnitt, wobei in der Steuerleitung (118) zwei Düsen (120, 122) angeordnet sind, und im Bereich zwischen den beiden Düsen (120, 122) eine zu einem in Öffnungsrichtung der Lenkungsdruckwaage (112) wirksamen Steuerraum führenden Steuerkanal (124) abzweigt, der über ein Rückschlagventil (126) mit einer den höchsten Lastdruck führenden LS-Leitung (60) verbunden ist. Die Steueranordnung lässt sich besonders einfach realisieren, wenn die Pumpe zur Druckmittelversorgung eine Konstantpumpe ist, der eine Bypass-Druckwaage zugeordnet ist, die in Öffnungsrichtung vom Pumpendruck und in Schließrichtung vom höchsten Lastdruck der Verbraucher beaufschlagt ist.In an alternative solution, the control line (118) leads from a pressure medium flow path upstream of the steering pressure balance (112) to a line section carrying the load pressure of the steering, wherein two nozzles (120, 122) are arranged in the control line (118) and in the area between the two two nozzles (120, 122) branches off to an effective in the opening direction of the steering pressure balance (112) control chamber control channel (124) which is connected via a check valve (126) with a highest load pressure leading LS line (60). The control arrangement can be implemented particularly easily if the pump for supplying pressure medium is a constant-displacement pump to which a bypass pressure compensator is assigned, which is acted upon in the opening direction by the pump pressure and in the closing direction by the highest load pressure of the consumers.
Die LS-Leitung kann zur Druckentlastung über ein Entlastungsventil mit einem Tank verbunden sein. Dieses Entlastungsventil ist als Stromregelventil ausgeführt.The LS line can be connected to a pressure relief valve via a relief valve with a tank. This relief valve is designed as a flow control valve.
Zur Absicherung der LS-Leitung kann in dieser ein LS-Druckbegrenzungsventil vorgesehen werden.To protect the LS line can be provided in this LS pressure relief valve.
Die eriϊndungsgemäße Steueranordnung wird vorzugsweise zur Ansteuerung eines Gabelstaplers eingesetzt, wobei ein LUDV-Ventil zur Steuerung der Hebenfunktion und ein LUDV-Ventil zur Steuerung des Neigens und des seitlichen Ver- schiebens eines Masts des Gabelstaplers vorgesehen sind.The control arrangement according to the invention is preferably used for controlling a forklift, wherein a LUDV valve for controlling the lifting function and a LUDV valve for controlling the tilting and the lateral displacement of a mast of the fork-lift truck are provided.
Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche.Other advantageous developments of the invention are the subject of further subclaims.
Im Folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:In the following preferred embodiments of the invention will be explained in more detail with reference to schematic drawings. Show it:
Figur 1 ein Schaltschema einer Steueranordnung eines Gabelstaplers mit einer Heben-, einer Neigen- und einer Verschiebenfunktion;Figure 1 is a circuit diagram of a control arrangement of a forklift truck with a lift, a tilt and a shift function;
Figur 2 eine Detaildarstellung der Steueranordnung aus Figur 1 ;Figure 2 is a detail of the control arrangement of Figure 1;
Figur 3 die Steueranordnung gemäß Figur 1 mit integrierter LS-Lenkung undFigure 3 shows the control arrangement of Figure 1 with integrated LS steering and
Figur 4 eine Variante der Schaltung gemäß Figur 3.FIG. 4 shows a variant of the circuit according to FIG. 3.
In Figur 1 ist ein Schaltschema einer hydraulischen Steueranordnung eines Gabelstaplers gezeigt. Diese Steueranordnung ist beispielsweise durch einen Mobilsteuerblock 1 ausgebildet, der im Wesentlichen aus einer LUDV-Sektion 2, zwei Wegeventilsektionen 4, 6 und einer Endplatte 8 besteht. Beim dargestellten Ausführungsbeispiel hat der Mobilsteuerblock 1 einen Druckanschluss P, einen Tankanschluss T sowie einen Arbeitsanschluss A an der LUDV-Sektion 2 und jeweils Arbeitsanschlüsse A, B an den beiden Wegeventilsektionen 4, 6. Der dargestellte Mobilsteuerblock 1 ist zur Ansteuerung eines Masts und der Gabel des Gabelstaplers vorgesehen, wobei über einen Hebezylinder 10 die Gabel angehoben oder abgesenkt werden kann. Ein Neigezylinder 12 ist zum Neigen des die Gabel führenden Mastes und ein Verschiebezylinder 14 zum seitlichen Verschieben des Masts vorgesehen. Der Hebezylinder 10 ist ein Differentialzylinder, wobei ein bodenseitiger Zylinderraum 16 über eine Arbeitsleitung 18 an den Arbeitsanschluss A der LUDV-Sektion 2 angeschlossen ist. Der Neigezylinder 12 ist als Doppelzylinder mit zwei parallel geschalteten Differentialzylindern ausgeführt, wobei die bodenseitigen Zylinderräume über eine Verbraucherleitung 20 und die beiden kolbenstangenseitigen Ringräume über eine weitere Verbraucherleitung 22 mit den Arbeitsanschlüssen B bzw. A der Wegeventilsektion 4 verbunden sind.FIG. 1 shows a circuit diagram of a hydraulic control arrangement of a fork-lift truck. This control arrangement is formed for example by a mobile control block 1, which consists essentially of a LUDV section 2, two-way valve sections 4, 6 and an end plate 8. In the illustrated embodiment, the mobile control block 1 has a pressure port P, a tank port T and a working port A at the LUDV section 2 and each working ports A, B at the two-way valve sections 4, 6. The illustrated mobile control block 1 is for driving a mast and the fork of the forklift provided, via a lifting cylinder 10, the fork can be raised or lowered. A tilting cylinder 12 is provided for tilting the fork leading the fork and a displacement cylinder 14 for laterally displacing the mast. The lifting cylinder 10 is a differential cylinder, wherein a bottom-side cylinder chamber 16 is connected via a working line 18 to the working port A of the LUDV section 2. The tilting cylinder 12 is designed as a double cylinder with two parallel-connected differential cylinders, wherein the bottom-side cylinder chambers are connected via a consumer line 20 and the two piston rod-side annular spaces via a further consumer line 22 to the working ports B and A of the directional valve section 4.
In der weiteren Verbraucherleitung 22 ist ein Senkbremsventil 24 angeordnet, das eine Druckmittelzufuhr vom Arbeitsanschluss A zu den beiden Ringräumen ungehindert zulässt und den Rücklauf von den beiden Ringräumen zum Arbeitsanschluss A hin drosselt, so dass ein kontrolliertes Neigen des Mastes ermöglicht wird. Derartige Senkbremsventile oder Counter-Balance-Ventile sind aus dem Stand der Technik bekannt, so dass weitere Erläuterungen entbehrlich sind.In the further consumer line 22, a lowering brake valve 24 is arranged, which allows a pressure medium supply from the working port A to the two annular spaces unhindered and throttles the return of the two annular spaces to the working port A, so that a controlled tilting of the mast is made possible. Such lowering brake valves or counter-balance valves are known from the prior art, so that further explanations are unnecessary.
Der Verschiebezylinder 14 ist als Gleichgangzylinder ausgeführt, wobei die beiden Ringräume über eine Arbeitsleitung 26 bzw. eine weitere Arbeitsleitung 28 mit den Arbeitsanschlüssen A, B der Wegeventilsektion 6 verbunden sind.The displacement cylinder 14 is designed as a synchronous cylinder, wherein the two annular spaces are connected via a working line 26 and a further working line 28 to the working ports A, B of the directional valve section 6.
In beiden Wegeventilsektionen 4, 6 ist jeweils ein 4/3-Wegeschaltventil 34 bzw. 32 vorgesehen, die in die dargestellte Sperrposition vorgespannt sind und über die - wie im Folgenden noch näher erläutert wird - die Druckmittelströmungsrichtung zu und von den Zylindern 12, 14 einstellbar ist.In both directional valve sections 4, 6, a 4/3-way switching valve 34 and 32 is respectively provided, which are biased in the blocking position shown and over - as will be explained in more detail - the pressure fluid flow direction to and from the cylinders 12, 14 adjustable is.
Die LUDV-Sektion 2 hat ein den beiden Zylindern 12, 14 zugeordnetes LUDV- Ventil 34, das aus einer Zumessblende 36 und einer dieser nachgeschalteten LUDV- Druckwaage 38 besteht. Bei derartigen LUDV-Ventilen 34 ist die LUDV-Druckwaage 38 in Richtung ihrer Schließposition durch den höchsten Lastdruck oder einen diesem etwa entsprechenden Druck und in Öffnungsrichtung von dem Druck stromabwärts der jeweiligen vorgeschalteten Zumessblende 36 beaufschlagt. Beim dargestellten Ausführungsbeispiel ist die Zumessblende 36 durch ein stetig verstellbares 2/2- Wegeventil ausgeführt, das in seine dargestellte Schließposition vorgespannt ist. Die Zumessblende kann durch Bestromen eines Proportionalmagneten 40 zur Einstellung des Druckmittelvolumenstroms zu den Verbrauchern 12, 14 geöffnet werden. Der Druckmittelvolumenstrom zum Hebezylinder 10 wird ebenfalls über ein LUDV- Ventil eingestellt, das im Folgenden als Heben-LUDV-Ventil 42 bezeichnet wird. Dessen Grundaufbau entspricht demjenigen des LUDV-Ventils 34 - es besteht somit im Wesentlichen aus einer Heben-Zumessblende 44 und einer dieser nachgeschalteten Heben-LUDV-Druckwaage 46. Die Heben-Zumessblende 44 ist ebenfalls durch ein stetig verstellbares 2/2-Wegeventil ausgeführt, deren Öffnungsquerschnitt wiederum über einen Proportionalmagneten 48 einstellbar ist. Wie im Folgenden noch näher erläutert wird, erfolgt das Anheben einer Last durch Zufuhr von Druckmittel in den bodenseitigen Zylinderraum 16 des Hebenzylinders 10. Das Absenken der Last oder der Gabel erfolgt alleine durch deren Gewichtskraft, wobei die Absenkgeschwindigkeit über ein LS-Ventil 50 gesteuert wird. Ein derartiges LS-Ventil besteht im Wesentlichen aus einer stetig verstellbaren LS-Zumessblende 52, der eine LS-Druckwaage 54 zugeordnet ist. Diese ist beim dargestellten Ausführungsbeispiel der LS-Zumessblende 52 vorgeschaltet und in Richtung seiner Schließposition durch die Kraft einer Feder und den Druck nach der LS-Zumessblende und in Öffnungsrichtung von dem Druck stromaufwärts der LS-Zumessblende 52 beaufschlagt. Beim dargestellten Ausführungsbeispiel ist die LS-Zumessblende 52 als 2/2-Wegesitzventil ausgeführt, das in seiner dargestellten Sperrposition eine leckagefreie Absperrung der Arbeitsleitung 18 ermöglicht. Die LS-Zumessblende 52 kann mittels eines Proportionalmagneten 56 oder von Hand eingestellt werden. Weitere Einzelheiten der beschriebenen LS-/LUDV- Ventile werden anhand Figur 2 erläutert.The LUDV section 2 has a LUDV valve 34 which is assigned to the two cylinders 12, 14 and which consists of a metering orifice 36 and a LUDV pressure compensator 38 connected downstream thereof. In such LUDV valves 34, the LUDV pressure compensator 38 is acted upon in the direction of its closed position by the highest load pressure or a pressure approximately corresponding thereto and in the opening direction by the pressure downstream of the respective upstream metering orifice 36. In the illustrated embodiment, the metering orifice 36 is designed by a continuously adjustable 2/2-way valve, which is biased in its closed position shown. The metering orifice can be opened by energizing a proportional magnet 40 for adjusting the pressure medium volume flow to the consumers 12, 14. The pressure medium volume flow to the lifting cylinder 10 is also set via a LUDV valve, which is referred to below as lifting LUDV valve 42. Its basic structure corresponds to that of the LUDV valve 34 - it thus essentially consists of a lifting metering orifice 44 and one of these downstream lifting LUDV pressure compensator 46. The lifting metering orifice 44 is also designed by a continuously adjustable 2/2-way valve, whose opening cross-section is in turn adjustable via a proportional magnet 48. As will be explained in more detail below, the lifting of a load by supplying pressure medium in the bottom-side cylinder chamber 16 of the lifting cylinder 10. The lowering of the load or the fork is done solely by their weight, the lowering speed is controlled by a LS-valve 50 , Such a LS-valve consists essentially of a continuously adjustable LS metering orifice 52, which is associated with a LS-pressure compensator 54. This is in the illustrated embodiment, the LS metering orifice 52 upstream and applied in the direction of its closed position by the force of a spring and the pressure after the LS metering orifice and in the opening direction of the pressure upstream of the LS metering orifice 52. In the illustrated embodiment, the LS metering orifice 52 is designed as a 2/2-way seat valve, which allows a leak-free shut-off of the working line 18 in its illustrated blocking position. The LS metering orifice 52 can be adjusted by means of a proportional solenoid 56 or by hand. Further details of the described LS / LUDV valves are explained with reference to FIG.
Der Druckanschluss P des Mobilsteuerblocks 1 ist an den Ausgangsanschluss einer LS-Pumpe ausgeführt, die beispielsweise als Konstantpumpe ausgebildet sein kann. Der Förderstrom dieser nicht dargestellten Konstantpumpe wird dann über eine Bypass-Druckwaage 58 eingestellt, die in Öffnungsrichtung vom Pumpendruck und in Schließrichtung vom höchsten Lastdruck aller Verbraucher und von der Kraft einer Druckwaagenfeder beaufschlagt ist. In der Regelposition der Bypass-Druckwaage 58 ist der Pumpendruck stets um ein der Kraft der Feder entsprechendes Pumpen- Δ oberhalb des höchsten Lastdrucks eingestellt, der in einer LS-Leitung 60 abgegriffen wird. Um die LS-Leitung 60 entlasten zu können, ist diese über ein als Stromregelventil ausgeführtes Entlastungsventil 62 mit einer an den Tankanschluss T des Mobilsteuerblocks 1 angeschlossenen Ablaufleitung 64 verbunden. Über dieses Entlastungsventil 62 strömt stets ein sehr geringer Steuerölstrom zum nicht dargestellten Tank ab. Zur Absicherung des Druckes in der LS-Leitung 60 ist ein LS- Druckbegrenzungsventil 66 vorgesehen. Weitere Einzelheiten der LUDV-Sektion 2 werden anhand der vergrößerten Darstellung in Figur 2 erläutert.The pressure port P of the mobile control block 1 is designed to the output port of a LS pump, which may be formed for example as a fixed displacement pump. The flow of this constant pump, not shown, is then adjusted via a bypass pressure compensator 58, which is acted upon in the opening direction by the pump pressure and in the closing direction of the highest load pressure of all consumers and by the force of a pressure compensator spring. In the control position of the bypass pressure compensator 58, the pump pressure is always adjusted by a force corresponding to the spring corresponding pump Δ above the highest load pressure, which is tapped in an LS line 60. In order to relieve the LS line 60, this is connected via a designed as a flow control valve relief valve 62 connected to the tank port T of the mobile control block 1 drain line 64. About this relief valve 62 always flows a very low control oil flow to the tank, not shown. To protect the pressure in the LS line 60, a LS pressure relief valve 66 is provided. Further details of the LUDV section 2 will be explained with reference to the enlarged view in FIG.
Das Druckmittel strömt vom Druckanschluss P über einen Zulaufkanal 68 zum Eingangsanschluss der Heben-Zumessblende 44 und der LUDV-Zumessblende 36. Der Ausgangsanschluss der LUDV-Zumessblende 36 ist über einen Druckwaagenkanal 70 mit dem Eingangsanschluss der LUDV-Druckwaage 38 verbunden, so dass diese in Öffnungsrichtung vom Druck stromabwärts der LUDV-Zumessblende 36 beaufschlagt ist. Wie vorstehend erwähnt, wird dieser Öffnungsquerschnitt über den Proportionalmagneten 40 eingestellt.The pressure medium flows from the pressure port P via an inlet channel 68 to the input port of the lifting metering orifice 44 and the LUDV metering orifice 36. The output port of the LUDV metering orifice 36 is connected via a pressure compensator channel 70 to the input port of the LUDV pressure compensator 38, so that these in Opening direction of the pressure downstream of the LUDV metering orifice 36 is acted upon. As mentioned above, this opening cross section is set via the proportional magnet 40.
Ein rückwärtiger Steuerraum 72 der LUDV-Druckwaage 38 ist an die LS-Leitung 60 angeschlossen, so dass auf die Rückseite des Druckwaagenkolbens der Druck in der LS-Leitung 60 in Schließrichtung wirkt. Da in dieser der höchste Lastdruck aller Verbraucher oder zumindest ein diesem entsprechender Druck anliegt, stellt sich am Eingang der LUDV-Druckwaage 38 in der Regelposition ebenfalls der höchste Lastdruck ein. Dieser höchste Lastdruck wird über die LUDV-Druckwaage 38 auf den tatsächlichen Lastdruck des zugeordneten Verbrauchers abgedrosselt und über die an den Ausgangsanschluss der LUDV-Druckwaage 38 angeschlossene Vorlaufleitung 74 zum zugeordneten Verbraucher geführt. In der Vorlaufleitung 74 ist ein in Richtung zu den beiden Zylindern 12, 14 öffnendes Rückschlagventil 76 angeordnet, so dass eine Druckmittelrückströmung zum LUDV-Ventil 34 verhindert wird. Das aus den Zylindern 12, 14 verdrängte Druckmittel strömt über den Ablaufkanal 64 und den Tankanschluss T zum Tank hin ab.A rear control chamber 72 of the LUDV pressure compensator 38 is connected to the LS line 60, so that acts on the back of the pressure compensator piston, the pressure in the LS line 60 in the closing direction. Since the highest load pressure of all consumers or at least a corresponding pressure is present in this, the highest load pressure also arises at the entrance of the LUDV pressure compensator 38 in the control position. This highest load pressure is throttled over the LUDV pressure compensator 38 to the actual load pressure of the associated consumer and guided via the connected to the output terminal of the LUDV pressure compensator 38 feed line 74 to the associated consumer. In the flow line 74 a in the direction of the two cylinders 12, 14 opening check valve 76 is arranged, so that a pressure medium backflow to the LUDV valve 34 is prevented. The displaced from the cylinders 12, 14 pressure fluid flows through the drain passage 64 and the tank port T to the tank down.
Das Heben-LUDV-Ventil 42 hat im Prinzip den gleichen Aufbau wie das LUDV- Ventil 34. Der Eingang der Heben-Zumessblende 44 ist an den Zulaufkanal 68 angeschlossen und der Ausgang über einen weiteren Druckwaagenkanal 74 mit dem Eingang der Heben-LUDV-Druckwaage 46 verbunden. Deren rückwärtiger Steuerraum 76 ist ebenfalls an die LS-Leitung 60 angeschlossen, so dass der Druckwaagenkolben der Heben-LUDV-Druckwaage 46 in Schließrichtung vom höchsten Lastdruck und in Öffnungsrichtung vom Druck stromabwärts der Heben-Zumessblende 44 beaufschlagt ist. Die Verstellung dieser Heben-Zumessblende 44 erfolgt über den Proportionalmagneten 48. Der Ausgangsanschluss der Heben-LUDV-Druckwaage 46 ist über einen Vorlaufkanal 82 und ein in Richtung zum Arbeitsanschluss A öffnendes Rückschlagventil 84 mit dem Arbeitsanschluss A verbunden. Im Bereich zwischen dem Arbeitsanschluss A und dem Rückschlagventil 84 zweigt vom Vorlaufkanal 82 ein Rücklaufkanal 86 ab, in dem das in Absenkrichtung wirksame LS-Ventil 50 angeordnet ist.The lift-LUDV valve 42 has in principle the same structure as the LUDV valve 34. The input of the lifting metering orifice 44 is connected to the inlet channel 68 and the output via a further pressure compensator channel 74 to the input of the lifting LUDV pressure compensator 46 connected. Their rear control chamber 76 is also connected to the LS line 60, so that the pressure compensator piston of the lifting LUDV pressure compensator 46 is acted upon in the closing direction by the highest load pressure and in the opening direction by the pressure downstream of the lifting metering orifice 44. The adjustment of this lifting metering orifice 44 takes place via the proportional magnet 48. The output connection of the lifting LUDV pressure compensator 46 is connected to the working connection A via a feed channel 82 and a check valve 84 which opens in the direction of the working connection A. In the area between the Working port A and the check valve 84 branches from the feed channel 82 from a return channel 86, in which the effective in the lowering direction LS-valve 50 is arranged.
Der Eingang der LS-Zulaufmessblende 52 ist an den Rücklaufkanal 86 angeschlossen. Der Ausgang ist über einen Druckwaagenkanal 88 mit dem Eingang der LS- Druckwaage 54 verbunden. Deren Druckwaagenkolben ist in Schließrichtung von der Kraft einer Feder 90 und dem Druck am Ausgang der LS-Zulaufmessblende 52 beaufschlagt. Dieser Steuerdruck wird über einen Steuerkanal 92 im Druckwaagenkanal 88 abgegriffen. In Öffnungsrichtung wirkt der Druck stromaufwärts der LS-Zulaufmessblende 52. Dieser Druck wird über einen Steuerkanal 94 abgegriffen, wobei ein Teil des Steuerölströmungspfades, in Figur 2 mit 94a gekennzeichnet, in die LS- Zumessblende 52 integriert ist. Wie bereits anhand Figur 1 erläutert, erfolgt die Einstellung des Öffnungsquerschnitts der LS-Zumessblende 52 über den Proportionalmagneten 56 oder von Hand über eine Handhabe 96.The input of the LS inlet orifice 52 is connected to the return channel 86. The output is connected via a pressure compensator channel 88 to the input of the LS-pressure compensator 54. Their pressure compensator piston is acted upon in the closing direction by the force of a spring 90 and the pressure at the outlet of the LS inlet orifice 52. This control pressure is tapped via a control channel 92 in the pressure compensator channel 88. In the opening direction, the pressure acts upstream of the LS Zulaufmessblende 52. This pressure is tapped via a control channel 94, wherein a part of the control oil flow path, indicated in Figure 2 with 94a, is integrated into the LS metering orifice 52. As already explained with reference to FIG. 1, the adjustment of the opening cross section of the LS metering orifice 52 takes place via the proportional magnet 56 or manually via a handle 96.
Über das LS-Ventil 50 wird der vom Heben-Zylinder 10 ablaufende Druckmittelvolumenstrom lastdruckunabhängig konstant gehalten. Wie bereits erläutert, ist die LS- Zumessblende 52 als Sitzventil ausgeführt, so dass in der dargestellten Schließposition eine leckagefreie Abstützung des Hebe-Zylinders 10 erfolgt. Zum Absenken der Last wird die LS-Zumeßblende 52 aufgesteuert, wobei die Absenkgeschwindigkeit lastdruckunabhängig konstant gehalten werden kann, da in der Regelposition der LS- Druckwaage 54 eine konstante, der Kraft der Feder 90 entsprechende Druckdifferenz über der LS-Zulaufmessblende 52 eingeregelt wird.About the LS-valve 50 running off the lifting cylinder 10 pressure medium flow rate is held constant load pressure independent. As already explained, the LS metering orifice 52 is designed as a seat valve, so that in the illustrated closed position a leakage-free support of the lifting cylinder 10 takes place. To lower the load, the LS Zumeßblende 52 is opened, the lowering speed can be kept constant load pressure, as in the control position of the LS pressure compensator 54 a constant, the force of the spring 90 corresponding pressure difference across the LS Zulaufmessblende 52 is adjusted.
Die Bypass-Druckwaage 58 ist, wie bereits erwähnt, durch die Kraft einer Druckwaagenfeder 98 und dem Druck in der LS-Leitung in Schließrichtung und in Öffnungsrichtung durch den Druck im Zulaufkanal 68 beaufschlagt, der über einen Kanal 100 abgegriffen ist. Das Entlastungsventil 62 und das LS-Druckbegrenzungs- ventil 66 erstrecken sich jeweils zwischen der LS-Leitung 60 und dem Ablaufkanal 64.The bypass pressure compensator 58 is, as already mentioned, acted upon by the force of a pressure compensator spring 98 and the pressure in the LS line in the closing direction and in the opening direction by the pressure in the inlet channel 68, which is tapped off via a channel 100. The relief valve 62 and the LS pressure relief valve 66 each extend between the LS line 60 and the drain channel 64.
Die in den Figuren 1 und 2 dargestellte Schaltung ermöglicht es, beispielsweise den Hebe-Zylinder 16 und entweder den Neigezylinder 12 oder den Verschiebezylinder 14 gleichzeitig zu betätigen.The circuit shown in Figures 1 and 2 makes it possible to operate, for example, the lifting cylinder 16 and either the tilting cylinder 12 or the displacement cylinder 14 at the same time.
Wie insbesondere aus Figur 1 hervorgeht, sind die beiden Zylinder 12, 14 parallel geschaltet, wobei vorgesehen ist, dass lediglich einer der beiden Verbraucher zugeschaltet wird. Die den beiden Zylindern 12, 14 vorgeschalteten Wegeventile 30, 32 sind jeweils als 4/3-Wegeventile ausgeführt und über einen Zentrierfederanordnung in ihre dargestellte Grundposition vorgespannt. Die Verstellung in die Schaltstellungen a, b erfolgt über Schaltmagnete. Beim Umschalten des Wegevntils 30 in die Schaltstellung a wird der Vorlaufkanal 74 mit dem Arbeitsanschluss A und die Ablaufleitung 64 mit dem Arbeitsanschluss B verbunden. Dadurch werden die beiden Neigezylinder 12 ausgefahren und die Mastneigung entsprechend verringert. Beim Umschalten des Wegeventils 32 in die Schaltstellung a wird dann entsprechend der Verschiebezylinder 14 gemäß der Darstellung in Figur 1 nach rechts verschoben.As can be seen in particular from FIG. 1, the two cylinders 12, 14 are connected in parallel, it being provided that only one of the two consumers is switched on. The two cylinders 12, 14 upstream directional control valves 30, 32 are each designed as 4/3-way valves and biased by a centering spring assembly in its illustrated basic position. The adjustment in the switching positions a, b via switching magnets. When switching the Wegevntils 30 in the switching position a of the flow channel 74 is connected to the working port A and the drain line 64 to the working port B. As a result, the two tilting cylinders 12 are extended and the mast tilt is correspondingly reduced. When switching the directional control valve 32 in the switching position a is then moved according to the displacement cylinder 14 as shown in Figure 1 to the right.
Beim Umschalten des Wegeventils 30 in die Schaltstellung b sind die beiden Arbeitsanschlüsse A, B der Zylinder 12 mit dem Vorlaufkanal 64 bzw. mit dem Vorlaufkanal 74 verbunden, so dass beispielsweise der Mast über den Neigezylinder 12 geneigt wird, wobei die Neigegeschwindigkeit über das im Rücklauf befindliche Senkbremsventil 24 bestimmt ist.When switching the directional control valve 30 in the switching position b, the two working ports A, B of the cylinder 12 are connected to the flow channel 64 and the feed channel 74 so that, for example, the mast is tilted over the tilting cylinder 12, wherein the tilting speed over that in the return located lowering brake valve 24 is determined.
Schaltet man das Wegeventil 32 in die Schaltstellung b, so wird der Verschiebezylinder 14 in der Darstellung gemäß Figur 1 nach links verschoben. Wie bereits erwähnt, wird stets entweder der Verschiebezylinder 14 oder der Neigezylinder 12 betätigt, so dass der entsprechende Verbraucher über das LU DV- Ventil 34 mit Druckmittel versorgt wird.If one switches the directional control valve 32 in the switching position b, the displacement cylinder 14 is shifted in the illustration of Figure 1 to the left. As already mentioned, either the displacement cylinder 14 or the tilting cylinder 12 is always actuated, so that the corresponding consumer is supplied with pressure medium via the LU DV valve 34.
Bei gleichzeitiger Betätigung des Hebezylinders 10 und des Neigezylinders 12 wird der Druckmittelvolumenstrom über die LUDV-Ventile 34 und 42 in Abhängigkeit vom eingestellten Öffnungsquerschnitt der Zumessblenden 44 und 36 konstant gehalten, wobei auch bei Untersättigung die Aufteilung des Druckmittelvolumenstroms lastunabhängig konstant bleibt, so dass auch dann noch beide Verbraucher 16, 12 oder 14 parallel angesteuert werden können. Wie eingangs beschrieben, ist dies bei herkömmlichen Steueranordnungen für Gabelstapler nicht möglich.With simultaneous actuation of the lifting cylinder 10 and the tilting cylinder 12, the pressure medium volume flow through the LUDV valves 34 and 42 depending on the set opening cross section of the metering orifices 44 and 36 kept constant, even at sub-saturation, the distribution of the pressure medium volume flow remains constant load independent, so even then still both consumers 16, 12 or 14 can be controlled in parallel. As described above, this is not possible with conventional control arrangements for forklifts.
In Figur 3 ist ein Ausführungsbeispiel dargestellt, bei dem in die Schaltung gemäß den Figuren 1 und 2 eine Lenkung 102 integriert ist. Eine derartige Lenkung hat üblicher weise einen Lenkzylinder 104, der zum Lenken über ein Lenkaggregat 106 mit Druckmittel versorgt wird. Derartige Lenkaggregate 106, auch Orbitrol genannt, sind beispielsweise im Datenblatt RD 14 365 der Bosch Rexroth AG beschrieben. Das Lenkaggregat 106 besteht im Wesentlichen aus einer Dosierpumpe und einem handbetätigtem Servoventil in Drehschieberbauweise. Die Baugröße der Dosierpumpe ist so gewählt, dass mit drei bis fünf Lenkradumdrehungen vom Anschlag zum Anschlag der Lenkung gelenkt werden kann. Über das Servoventil wird dabei eine Zumessblende eingestellt. Die Druckmittelversorgung des Lenkaggregats 106 erfolgt über eine vom Zulaufkanal 68 abzweigende Lenkleitung 108, die über einen Lenkanschluss C und eine Arbeitsleitung 110 mit dem Lenkaggregat 106 verbunden ist. In der Lenkleitung 108 ist eine Lenkungsdruckwaage 112 angeordnet, die gemeinsam mit der ins Lenkaggregat 106 integrierten Zumessblende ein LS-Ventil ausbildet, über das der Druckmittelvolumenstrom zur Verstellung des Lenkzylinders 104 lastunabhängig konstant gehalten werden kann.FIG. 3 shows an exemplary embodiment in which a steering system 102 is integrated into the circuit according to FIGS. 1 and 2. Such steering usually has a steering cylinder 104 which is supplied for steering via a steering unit 106 with pressure medium. Such steering units 106, also called Orbitrol, are described for example in the data sheet RD 14 365 Bosch Rexroth AG. The steering unit 106 consists essentially of a metering pump and a hand-operated servo valve in rotary valve construction. The size of the metering pump is chosen so that with three to five steering wheel turns from the stop to the stop of the steering can be steered. About the servo valve while a metering orifice is set. The pressure medium supply of the steering unit 106 via a branched off from the inlet channel 68 steering line 108 which is connected via a steering port C and a working line 110 to the steering unit 106. In the steering line 108, a steering pressure compensator 112 is arranged, which forms an LS valve together with the integrated into the steering unit 106 metering orifice, via which the pressure medium flow rate for adjusting the steering cylinder 104 can be kept constant independent of load.
Die Lenkungsdruckwaage 112 ist in Schließrichtung vom Druck stromaufwärts, d.h. vom Druck im Bereich des Anschlusses C beaufschlagt. Dieser Steuerdruck wird über eine Lenksteuerleitung 114 abgegriffen. In Öffnungsrichtung wirkt auf die Lenkungsdruckwaage 112 eine einstellbare Druckwaagenfeder 116 sowie ein Lenksteuerdruck, der an einer Steuerleitung 118 abgegriffen ist. Diese erstreckt sich vom Lenkaggregat 106 bis zu einem stromaufwärts der Lenkungsdruckwaage 112 gelegenen Abschnitts der Lenkleitung 108. Über diese Steuerleitung 118 kann der Lastdruck der Lenkung abgegriffen werden. Beim dargestellten Ausführungsbeispiel sind in der Steuerleitung 118 zwei Düsen 120, 122 angeordnet, die gemeinsam einen Druckteiler bilden. Im Bereich zwischen den beiden Düsen 120, 122 zweigt ein Steuerkanal 124 ab, der auch mit einem federseitigen Steuerraum der Lenkungsdruckwaage 112 verbunden ist, so dass der Druck im Steuerkanal 124 in Öffnungsrichtung auf den Kolben der Lenkungsdruckwaage 112 wirkt. Beim dargestellten Ausführungsbeispiel ist der Steuerkanal 124 über ein weiteres Rückschlagventil 126 mit der LS-Leitung 60 verbunden.The steering pressure gauge 112 is in the closing direction from the upstream pressure, i. acted upon by the pressure in the region of the terminal C. This control pressure is tapped via a steering control line 114. In the opening direction acts on the steering pressure compensator 112, an adjustable pressure compensator spring 116 and a steering control pressure, which is tapped on a control line 118. This extends from the steering unit 106 to an upstream of the steering pressure balance 112 located portion of the steering line 108. About this control line 118, the load pressure of the steering can be tapped. In the illustrated embodiment, two nozzles 120, 122 are arranged in the control line 118, which together form a pressure divider. In the area between the two nozzles 120, 122 branches off a control channel 124 which is also connected to a spring-side control chamber of the steering pressure balance 112, so that the pressure in the control channel 124 acts in the opening direction on the piston of the steering pressure balance 112. In the illustrated embodiment, the control channel 124 is connected via a further check valve 126 to the LS line 60.
Die in Figur 3 untere Düse 122 bildet bei betätigter Lenkung gemeinsam mit der Bypass-Druckwaage 58 einen Stromregler, über die der Steuerölvolumenstrom über die Düse 122 konstant gehalten werden kann. Durch geeignete Auslegung der weiteren Düse 120 kann dann im Bereich zwischen den Düsen 120, 122 ein vorbestimmter Druck eingestellt werden, der um eine gewisse Druckdifferenz oberhalb des Lenkungslastdrucks liegt. Mit einer derartigen Schaltung ist gewährleistet, dass bei einer Untersättigung die Lenkung 102 mit Druckmittel versorgt wird, wobei über den beiden Zumessblenden 36 und 44 der LUDV-Verbraucher 10, 12, 14 kein Δ ansteht, da bei geeigneter Wahl der Düse 120 am Eingang der zugehörigen LUDV-Druckwaage 38, 46 der gleiche Druck wie in dem Steuerkanal 124 eingeregelt ist und dieser Druck bei geeigneter Düsenwahl (Düse 120) dem Pumpendruck entspricht, so dass kein Druckmittel oder nur ein geringer Volumenstrom zu den sonstigen LUDV-Verbrauchern strömt, die Lenkung aber voll funktionsfähig bleibt.The lower nozzle 122 in FIG. 3, together with the bypass pressure compensator 58, forms a current regulator when the steering is actuated, by means of which the control oil volume flow via the nozzle 122 can be kept constant. By suitable design of the further nozzle 120, a predetermined pressure can then be set in the area between the nozzles 120, 122, which is a certain pressure difference above the steering load pressure. With such a circuit it is ensured that at a supersaturation, the steering 102 is supplied with pressure medium, wherein above the two orifices 36 and 44 of the LUDV consumers 10, 12, 14 no Δ is present, since with a suitable choice of the nozzle 120 at the entrance of associated LUDV pressure compensator 38, 46, the same pressure as in the control channel 124 is adjusted and this pressure with a suitable nozzle selection (nozzle 120) corresponds to the pump pressure, so that no Pressure medium or only a small volume flow to the other LUDV consumers flows, but the steering remains fully functional.
Eine weitere Besonderheit des in Figur 3 dargestellten Ausführungsbeispiels besteht darin, dass im Vorlaufkanal 74 ein Druckreduzierventil 128 vorgesehen ist, über das in den Wegeventilsektionen 4, 6 ein geringerer Arbeitsdruck als in der LUDV- Sektion 2 eingestellt werden kann. Das Druckreduzierventil 128 ist vorzugsweise im Bereich zwischen der LUDV-Druckwaage 38 und dem Rückschlagventil 76 angeordnet.Another special feature of the embodiment shown in Figure 3 is that in the flow channel 74, a pressure reducing valve 128 is provided, via which in the directional control valve sections 4, 6, a lower working pressure than in the LUDV section 2 can be set. The pressure reducing valve 128 is preferably arranged in the region between the LUDV pressure compensator 38 and the check valve 76.
Figur 4 zeigt eine weitere Möglichkeit, die Lenkung 102 in die Schaltung gemäß Figur 1 zu integrieren, wobei die Unterschiede zwischen den Ausführungsbeispielen in Figur 3 und 4 lediglich im Abgriff des auf die Lenkungsdruckwaage 112 wirkenden Lastdrucks liegen.FIG. 4 shows a further possibility of integrating the steering system 102 into the circuit according to FIG. 1, wherein the differences between the exemplary embodiments in FIGS. 3 and 4 lie merely in the tapping of the load pressure acting on the steering pressure compensator 112.
Bei der in Figur 4 dargestellten Variante wird der Lastdruck des Lenkaggregats 106 über einen Kanal 130 abgegriffen, der im Unterschied zur Steuerleitung 118 aus dem vorbeschriebenen Ausführungsbeispiel keine Verbindung zur Lenkleitung 108 hat. Der Steuerkanal 124 verbindet bei diesem Ausführungsbeispiel die LS-Leitung 60 mit der Arbeitsleitung 110, so dass der Druck stromabwärts der Lenkungsdruckwaage 112 über das Rückschlagventil 126 in die LS-Leitung 60 gemeldet wird. Dieser Druck ist höher als der Lastdruck der Lenkung. Auf die Lenkungsdruckwaage 112 wirkt in Öffnungsrichtung wiederum die Druckwaagenfeder 116 und der Druck in dem Kanal 130. Dieser Druck entspricht etwa dem Lastdruck der Lenkung (Druck stromabwärts der Lenkungszumessblende).In the variant shown in Figure 4, the load pressure of the steering unit 106 is tapped via a channel 130, which has no connection to the steering line 108 in contrast to the control line 118 from the above-described embodiment. The control channel 124 connects in this embodiment, the LS line 60 to the working line 110, so that the pressure downstream of the steering pressure gauge 112 is reported via the check valve 126 in the LS line 60. This pressure is higher than the load pressure of the steering. In turn, the pressure balance spring 116 and the pressure in the channel 130 act on the steering pressure balance 112 in the opening direction. This pressure corresponds approximately to the load pressure of the steering (pressure downstream of the steering metering orifice).
Im Fall eine Untersättigung, d.h. dann, wenn die Pumpe nicht genügend Druckmittel fördern kann, sinkt der Druck im Zulaufkanal 68 ab und über die LUDV- Druckwaagen liegt der jeweilige Lastdruck der LUDV-Verbraucher am Ausgang der Zulaufmessblende an, so dass entsprechend die Druckdifferenz über den LUDV- Messblenden absinkt und weniger Druckmittel zu den LUDV-Verbrauchern strömt oder diese nicht mehr mit Druckmittel versorgt werden. Das Lenkaggregat 106 wird jedoch bei vollständig geöffneter Lenkungsdruckwaage 112 mit Druckmittel versorgt, so dass die Lenkung weiterhin betätigt werden kann. Eine derartige Integration einer Lenkung in eine LUDV-Steueranordnung ist per se aus der DE 101 19 276 A1 bekannt, so dass weitere Ausführungen entbehrlich sind. Prinzipiell können die vorbeschriebenen Steueranordnungen auch bei anderen mobilen Arbeitsmaschinen, wie beispielsweise Radladern, Minibaggern, etc. angewendet werden.In the case of a supersaturation, ie when the pump can not deliver enough pressure medium, the pressure in the inlet channel 68 decreases and the respective load pressure of the LUDV consumers is applied to the outlet metering orifice via the LUDV pressure compensators, so that the pressure difference correspondingly exceeds the LUDV orifices fall and less pressure fluid flows to the LUDV consumers or these are no longer supplied with pressure medium. However, the steering unit 106 is supplied with pressure medium fully open steering pressure balance 112, so that the steering can still be operated. Such integration of a steering in a LUDV control arrangement is known per se from DE 101 19 276 A1, so that further embodiments are unnecessary. In principle, the above-described control arrangements can also be applied to other mobile machines, such as wheel loaders, mini excavators, etc.
Offenbart ist eine hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Gabelstapler, mit zumindest zwei hydraulischen Verbrauchern, von denen einer einer Hebenfunktion hat. Erfindungsgemäß sind die beiden Verbraucher jeweils über ein LUDV-Ventil mit Zulaufmessblende und nachgeschalteter LUDV-Druckwaage angesteuert. Disclosed is a hydraulic control arrangement for a mobile work machine, in particular for a forklift, with at least two hydraulic consumers, one of which has a lifting function. According to the invention, the two consumers are each controlled via a LUDV valve with inlet orifice plate and downstream LUDV pressure compensator.
Bezuqszeichenliste:LIST OF REFERENCES:
1 Steuerblock1 control block
2 LUDV-Sektion2 LUDV section
4 Wegeventilsektion4 way valve section
6 Wegeventilsektion6 way valve section
8 Endplatte8 end plate
10 Hebezylinder10 lifting cylinders
12 Neigezylinder12 tilt cylinders
14 Verschiebezylinder14 displacement cylinder
16 Zylinderraum16 cylinder space
18 Arbeitsleitung18 work management
20 Verbraucherleitung20 consumer guidance
22 weitere Verbraucherleitung22 more consumer line
24 Senkbremsventil24 lowering brake valve
26 Arbeitsleitung26 work management
28 Arbeitsleitung28 work management
30 Wegeventil30 way valve
32 Wegeventil32 way valve
34 LUDV-Ventil34 LUDV valve
36 LUDV-Zumessblende36 LUDV metering orifice
38 LU DV-Druckwaage38 LU DV pressure balance
40 Proportionalmagnet40 proportional magnet
42 Heben-LUDV-Ventil42 lifting LUDV valve
44 Heben-Zumessblende44 Lifting orifice
46 Heben-LU DV-Druckwaage46 Lift-LU DV pressure balance
48 Proportionalmagnet48 proportional magnet
50 LS-Ventil50 LS valve
52 LS-Zumessblende52 LS metering orifice
54 LS-Druckwaage54 LS pressure compensator
56 Proportionalmagnet56 Proportional magnet
58 Bypass-Druckwaage58 Bypass pressure balance
60 LS-Leitung60 LS line
62 Entlastungsventil62 relief valve
64 Ablaufleitung64 drain line
66 LS-Druckbegrenzungsventil Zulaufkanal66 LS pressure relief valve inlet channel
DruckwaagenkanalPressure balance channel
Steuerraumcontrol room
Vorlaufkanalforward channel
Rückschlagventilcheck valve
Steuerraumcontrol room
Vorlaufkanalforward channel
Vorlaufkanalforward channel
Rückschlagventilcheck valve
RücklaufkanalReturn channel
DruckwaagenkanalPressure balance channel
Federfeather
Steuerkanalcontrol channel
Steuerkanalcontrol channel
Handhabehandle
DruckwaagenfederCompensator spring
Kanalchannel
Lenkungsteering
Lenkzylindersteering cylinder
Lenkaggregatsteering unit
Lenkleitungsteering line
Arbeitsleitungworking line
LenkungsdruckwaageSteering pressure
LenksteuerleitungSteering control line
DruckwaagenfederCompensator spring
Steuerleitungcontrol line
Düsejet
Düsejet
Steuerkanal weiteres RückschlagventilControl channel further check valve
DruckreduzierventilPressure reducing valve
Kanal channel

Claims

Patentansprüche claims
1. Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, mit zumindest zwei hydraulischen Verbrauchern (10, 12, 14), die von einer Pumpe in Abhängigkeit vom höchsten Lastdruck mit Druckmittel versorgbar sind, wobei der Druckmittelvolumenstrom zu einem der Verbraucher (10) für eine Hebefunktion und zu einem eine andere Funktion der Arbeitsmaschine betätigenden Verbraucher (12, 14) über jeweils eine Zulaufmessblende (36, 44) und einer dieser zugeordnete LUDV-Druckwaage (38, 46) bestimmt ist, die jeweils in Öffnungsrichtung vom Druck stromabwärts der zugeordneten Zulaufmessblende (36, 44) und in Schließrichtung von einem etwa dem höchsten Lastdruck der Verbraucher (10, 12, 14) entsprechenden Druck beaufschlagt ist.1. Hydraulic control arrangement for a mobile work machine, with at least two hydraulic consumers (10, 12, 14) which can be supplied by a pump in response to the highest load pressure with pressure medium, wherein the pressure medium volume flow to one of the consumers (10) for a lifting function and to a different function of the working machine actuated consumer (12, 14) via one inlet orifice (36, 44) and one of these associated LUDV pressure compensator (38, 46) is determined, each in the opening direction of the pressure downstream of the associated inlet orifice (36 , 44) and in the closing direction is acted upon by a pressure corresponding approximately to the highest load pressure of the consumer (10, 12, 14).
2. Hydraulische Steueranordnung nach Patentanspruch 1 , wobei ein weiterer Verbraucher, beispielsweise zum Neigen eines Mastes, über ein Proportionalventil angesteuert ist.2. Hydraulic control arrangement according to claim 1, wherein a further consumer, for example, for tilting a mast, is controlled via a proportional valve.
3. Hydraulische Steueranordnung nach Patentanspruch 1 , wobei eine Zulaufmessblende (36) und die dazu gehörige LUDV-Druckwaage (38) zumindest zwei Verbrauchern (12, 14) zugeordnet ist.3. Hydraulic control arrangement according to claim 1, wherein a Zulaufmessblende (36) and the associated LUDV pressure compensator (38) is associated with at least two consumers (12, 14).
4. Hydraulische Steueranordnung nach Patentanspruch 3, wobei zumindest einem der Verbraucher (12, 14) ein Wegeventil (30, 32) zur Einstellung der Druckmittelströmungsrichtung zum und vom Verbraucher (12, 14) zugeordnet ist.4. Hydraulic control arrangement according to claim 3, wherein at least one of the consumers (12, 14) is assigned a directional control valve (30, 32) for adjusting the pressure fluid flow direction to and from the consumer (12, 14).
5. Hydraulische Steueranordnung nach einem der vorhergehenden Patentansprüche, wobei die Zulaufmessblende (36, 44) durch ein stetig verstellbares 2-We- geventil gebildet ist.5. Hydraulic control arrangement according to one of the preceding claims, wherein the inlet orifice (36, 44) is formed by a continuously adjustable 2-way ge- valve.
6. Hydraulische Steueranordnung nach einem der Patentansprüche 3 bis 5, wobei stromabwärts der LUDV-Druckwaage (38) ein Druckreduzierventil (128) vorgesehen ist.6. Hydraulic control arrangement according to one of the claims 3 to 5, wherein downstream of the LUDV pressure compensator (38), a pressure reducing valve (128) is provided.
7. Hydraulische Steueranordnung nach einem der vorhergehenden Patentansprüche, wobei im Rücklauf von dem für das Heben vorgesehene Verbraucher (10) zur Steuerung des Absenkens ein LS-Ventil (50) mit LS-Zumessblende (52) und LS- Druckwaage (54) angeordnet ist, wobei stromabwärts der LUDV-Druckwaage (46) dieses Verbrauchers (10) ein in Richtung zu diesem öffnendes Rückschlagventil (84) angeordnet ist und ein Rücklaufkanal (86) zwischen dem Rückschlagventil (84) und dem Verbraucher (10) abzweigt.7. A hydraulic control arrangement according to one of the preceding claims, wherein in the return of the intended for lifting consumer (10) for controlling the lowering an LS-valve (50) with LS metering orifice (52) and LS- Pressure compensator (54) is arranged, wherein downstream of the LUDV pressure compensator (46) of this consumer (10) is arranged towards this opening check valve (84) and a return channel (86) between the check valve (84) and the consumer (10 ) branches off.
8. Hydraulische Steueranordnung nach einem der vorhergehenden Patentansprüche, mit einem Lenkaggregat (120), das eine LS-Zulaufmessblende zur Druckmittelversorgung eines Stellgliedes (104) der Lenkung (102) hat und dem eine Lenkungsdruckwaage (112) zugeordnet ist.8. A hydraulic control arrangement according to one of the preceding claims, comprising a steering unit (120) having an LS inlet orifice plate for supplying pressure medium to an actuator (104) of the steering (102) and which is associated with a steering pressure compensator (112).
9. Hydraulische Steueranordnung nach Patentanspruch 8, wobei die Lenkungsdruckwaage (112) in Schließrichtung vom Druck vor der LS-Zulaufmessblende des Lenkaggregats (106) und in Öffnungsrichtung von einer Feder (116) und dem Druck in einer Steuerleitung (118, 130) beaufschlagt ist, die mit einem den Lastdruck der Lenkung führenden Leitungsabschnitt verbunden ist.9. A hydraulic control arrangement according to claim 8, wherein the steering pressure compensator (112) in the closing direction by the pressure in front of the LS inlet orifice of the steering unit (106) and in the opening direction of a spring (116) and the pressure in a control line (118, 130) is acted upon which is connected to a line section carrying the load pressure of the steering.
10. Hydraulische Steueranordnung nach Patentanspruch 9, wobei ein stromabwärts der Lenkungsdruckwaage (112) gelegener Leitungsabschnitt über einen Steuerkanal (124) und ein in Richtung zum Lenkaggregat (106) sperrendes Rückschlagventil mit einer den höchsten Lastdruck der Verbraucher (10, 12, 14) führenden LS-Leitung (60) verbunden ist.10. A hydraulic control arrangement according to claim 9, wherein a downstream of the steering pressure compensator (112) located line section via a control channel (124) and in the direction of the steering unit (106) blocking check valve with a highest load pressure of the consumer (10, 12, 14) leading LS line (60) is connected.
11. Hydraulische Steueranordnung nach Patentanspruch 9, wobei die Steuerleitung (118) von einem Druckmittelströmungspfad stromaufwärts der Lenkungsdruckwaage (112) zu einem den Lastdruck der Lenkung führenden Leitungsabschnitt, wobei in der Steuerleitung (118) zwei Düsen (120, 122) angeordnet sind, und im Bereich zwischen den beiden Düsen (120, 122) eine zu einem in Öffnungsrichtung der Lenkungsdruckwaage (112) wirksamen Steuerraum führender Steuerkanal (124) abzweigt, der über ein Rückschlagventil (126) mit einer den höchsten Lastdruck führenden LS-Leitung (60) verbunden ist.11. A hydraulic control arrangement according to claim 9, wherein the control line (118) from a pressure fluid flow path upstream of the steering pressure balance (112) leading to a load pressure of the steering line portion, wherein in the control line (118) two nozzles (120, 122) are arranged, and in the area between the two nozzles (120, 122) branches off to a in the opening direction of the steering pressure balance (112) effective control chamber leading control channel (124) connected via a check valve (126) having a highest load pressure leading LS line (60) is.
12. Hydraulische Steueranordnung nach einem der vorhergehenden Patentansprüche, wobei die Pumpe eine Konstantpumpe ist, der eine Bypass-Druckwaage (58) zugeordnet ist, die in Öffnungsrichtung vom Pumpendruck und in Schließrichtung vom höchsten Lastdruck in der LS-Leitung (60) und einer Druckwaagenfeder beaufschlagt ist. 12. A hydraulic control arrangement according to one of the preceding claims, wherein the pump is a fixed displacement pump, which is associated with a bypass pressure compensator (58) in the opening direction of the pump pressure and in the closing direction of the highest load pressure in the LS line (60) and a pressure compensator spring is charged.
13. Hydraulische Steueranordnung nach Patentanspruch 8 oder 9, wobei die LS- Leitung (60) über ein Entlastungsventil (62) mit einem Tank verbunden ist.13. Hydraulic control arrangement according to claim 8 or 9, wherein the LS line (60) via a discharge valve (62) is connected to a tank.
14. Hydraulische Steueranordnung nach einem der Patentansprüche 8, 9 oder 11 , wobei der Druck in der LS-Leitung (60) über ein LS-Druckbegrenzungsventil (66) begrenzt ist.14. Hydraulic control arrangement according to one of the claims 8, 9 or 11, wherein the pressure in the LS line (60) via an LS-pressure relief valve (66) is limited.
15. Hydraulische Steueranordnung nach einem der vorhergehenden Patentansprüche, wobei die mobile Arbeitsmaschine ein Gabelstapler ist, wobei ein Hebezylinder (10) zum Anheben einer Last, ein Neigezylinder (12) zum Neigen und ein Verschiebezylinder (14) zum Seitenverschieben eines Masts vorgesehen sind, wobei den beiden letztgenannten Verbrauchern vorzugsweise ein gemeinsames LUDV-Ventil (34) zugeordnet ist. 15. A hydraulic control arrangement according to one of the preceding claims, wherein the mobile work machine is a forklift, wherein a lifting cylinder (10) for lifting a load, a tilting cylinder (12) for tilting and a displacement cylinder (14) are provided for side displacement of a mast, wherein the two latter consumers preferably associated with a common LUDV valve (34).
EP08734422A 2007-03-27 2008-03-20 Hydraulic control arrangement Not-in-force EP2142808B1 (en)

Applications Claiming Priority (3)

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DE102007014673 2007-03-27
DE102007028864A DE102007028864A1 (en) 2007-03-27 2007-06-22 Hydraulic control arrangement
PCT/DE2008/000491 WO2008116451A1 (en) 2007-03-27 2008-03-20 Hydraulic control arrangement

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EP2142808A1 true EP2142808A1 (en) 2010-01-13
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US (1) US8915075B2 (en)
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AT (1) ATE544954T1 (en)
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EP2142808B1 (en) 2012-02-08
US20100212308A1 (en) 2010-08-26
ATE544954T1 (en) 2012-02-15
WO2008116451A1 (en) 2008-10-02
DE102007028864A1 (en) 2008-10-02
US8915075B2 (en) 2014-12-23

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