EP2142808B1 - Hydraulic control arrangement - Google Patents
Hydraulic control arrangement Download PDFInfo
- Publication number
- EP2142808B1 EP2142808B1 EP08734422A EP08734422A EP2142808B1 EP 2142808 B1 EP2142808 B1 EP 2142808B1 EP 08734422 A EP08734422 A EP 08734422A EP 08734422 A EP08734422 A EP 08734422A EP 2142808 B1 EP2142808 B1 EP 2142808B1
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- EP
- European Patent Office
- Prior art keywords
- pressure
- steering
- valve
- line
- control arrangement
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- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/003—Systems with load-holding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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 changes in all metering orifices in the same way, if the pump pressure is lower at unsaturation - thus ensuring a proportional flow distribution of the flow to the consumers, so that, for example, an unloaded Fork of a forklift truck can be raised 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 forklift are provided.
- FIG. 1 a circuit diagram of a hydraulic control arrangement of a forklift is shown.
- 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 an LUDV valve 34 which is assigned to the two cylinders 12, 14 and 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 212-way valve, which is biased in its illustrated closed position.
- 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 consists essentially 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 the LS metering orifice upstream 52 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 leakage-free shutoff 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 based on FIG. 2 explained.
- 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. About this relief valve 62 always flows a very low control oil flow to the tank, not shown.
- a LS pressure relief valve 66 is provided to protect the pressure in the LS line 60.
- 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 another 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 Zulaufmessbrende 52.
- This pressure is tapped via a control channel 94, wherein a part of the control oil flow path, in FIG. 2 labeled 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 by hand 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 independent, since 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.
- FIGS. 1 and 2 illustrated circuit makes it possible, for example, the lifting cylinder 16 and either the tilting cylinder 12 or the displacement cylinder 14 to operate simultaneously.
- 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 corresponding to the displacement cylinder 14 as shown in FIG FIG. 1 moved 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 an embodiment is shown in which in the circuit according to the FIGS. 1 and 2 a steering 102 is integrated.
- a steering 102 is integrated.
- 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.
- lower nozzle 122 forms when actuated steering together with the bypass pressure compensator 58 a flow regulator, via which the control oil volume flow through the nozzle 122 can be kept constant.
- 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.
- FIG. 3 illustrated embodiment Another special feature of in FIG. 3 illustrated embodiment 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.
- FIG. 4 shows another way, the steering 102 in the circuit according to FIG. 1 integrate the differences between the embodiments in FIG. 3 and 4 lie only in the tap of the load pressure acting on the steering pressure balance 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 via the LUDV pressure compensators at the outlet of the inlet orifice, so that corresponding to the pressure difference over the LUDV measuring orifices sinks and less pressure medium 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.
- 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.
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- Physics & Mathematics (AREA)
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- Forklifts And Lifting Vehicles (AREA)
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Abstract
Description
Die Erfindung betrifft eine hydraulische Steueranordnung für eine mobile Arbeitsmaschine mit zumindest zwei hydraulischen Verbrauchern, von denen einer für eine Hebefunktion vorgesehen istThe 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
Beispiele sind in Dokument
In der
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 Unterversorgung 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 case of a shortage ie, in the case where 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 as 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
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 gleicher Weise 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 changes in all metering orifices in the same way, if the pump pressure is lower at unsaturation - thus ensuring a proportional flow distribution of the flow to the consumers, so that, for example, an unloaded Fork of a forklift truck can be raised 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.In a simply constructed solution, it may be sufficient if another consumer is controlled via a proportional valve.
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 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.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).
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.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 erfindungsgemäße 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 Verschiebens 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 forklift 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:
-
ein Schaltschema einer Steueranordnung eines Gabelstaplers mit einer Heben-, einer Neigen- und einer Verschiebenfunktion;Figur 1 -
eine Detaildarstellung der Steueranordnung ausFigur 2 ;Figur 1 -
Figur 3 die Steueranordnung gemäß mit integrierter LS-Lenkung undFigur 1 -
eine Variante der Schaltung gemäßFigur 4Figur 3 .
-
FIG. 1 a schematic diagram of a control arrangement of a forklift with a lift, a tilt and a shift function; -
FIG. 2 a detailed representation of the control arrangementFIG. 1 ; -
FIG. 3 the control arrangement according toFIG. 1 with integrated LS steering and -
FIG. 4 a variant of the circuit according toFIG. 3 ,
In
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
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
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
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 212-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.The
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 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. Die LS-Zumessblende 52 ist 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
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.The pressure port P of the
Weitere Einzelheiten der LUDV-Sektion 2 werden anhand der vergrößerten Darstellung in
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
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
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-
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
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-
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-Druckbegrenzungsventil 66 erstrecken sich jeweils zwischen der LS-Leitung 60 und dem Ablaufkanal 64.The
Die in den
Wie insbesondere aus
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
Schaltet man das Wegeventil 32 in die Schaltstellung b, so wird der Verschiebezylinder 14 in der Darstellung gemäß
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
In
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
Die in
Eine weitere Besonderheit des in
Bei der in
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
Prinzipiell können die vorbeschriebenen Steueranordnungen auch bei anderen mobilen Arbeitsmaschinen, wie beispielsweise Radladern, Minibaggern, etc. angewendet werden.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.
- 11
- Steuerblockcontrol block
- 22
- LUDV-SektionLUDV section
- 44
- WegeventilsektionDirectional control valve section
- 66
- WegeventilsektionDirectional control valve section
- 88th
- Endplatteendplate
- 1010
- Hebezylinderlifting cylinder
- 1212
- Neigezylindertilt cylinder
- 1414
- Verschiebezylinderdisplacement cylinder
- 1616
- Zylinderraumcylinder space
- 1818
- Arbeitsleitungworking line
- 2020
- Verbraucherleitungconsumer line
- 2222
- weitere Verbraucherleitungfurther consumer guidance
- 2424
- Senkbremsventillowering valve
- 2626
- Arbeitsleitungworking line
- 2828
- Arbeitsleitungworking line
- 3030
- Wegeventilway valve
- 3232
- Wegeventilway valve
- 3434
- LUDV-VentilLIFD valve
- 3636
- LUDV-ZumessblendeLUDV metering orifice
- 3838
- LUDV-DruckwaageLUDV pressure
- 4040
- Proportionalmagnetproportional solenoid
- 4242
- Heben-LUDV-VentilLift-LIFD valve
- 4444
- Heben-ZumessblendeLift-metering orifice
- 4646
- Heben-LUDV-DruckwaageLift-LUDV pressure
- 4848
- Proportionalmagnetproportional solenoid
- 5050
- LS-VentilLS-valve
- 5252
- LS-ZumessblendeLS metering orifice
- 5454
- LS-DruckwaageLS pressure
- 5656
- Proportionalmagnetproportional solenoid
- 5858
- Bypass-DruckwaageBypass pressure compensator
- 6060
- LS-LeitungLS line
- 6262
- Entlastungsventilrelief valve
- 6464
- Ablaufleitungdrain line
- 6666
- LS-DruckbegrenzungsventilLS pressure relief valve
- 6868
- Zulaufkanalinlet channel
- 7070
- DruckwaagenkanalPressure balance channel
- 7272
- Steuerraumcontrol room
- 7474
- Vorlaufkanalforward channel
- 7676
- Rückschlagventilcheck valve
- 7878
- Steuerraumcontrol room
- 8080
- Vorlaufkanalforward channel
- 8282
- Vorlaufkanalforward channel
- 8484
- Rückschlagventilcheck valve
- 8686
- RücklaufkanalReturn channel
- 8888
- DruckwaagenkanalPressure balance channel
- 9090
- Federfeather
- 9292
- Steuerkanalcontrol channel
- 9494
- Steuerkanalcontrol channel
- 9696
- Handhabehandle
- 9898
- DruckwaagenfederCompensator spring
- 100100
- Kanalchannel
- 102102
- Lenkungsteering
- 104104
- Lenkzylindersteering cylinder
- 106106
- Lenkaggregatsteering unit
- 108108
- Lenkleitungsteering line
- 110110
- Arbeitsleitungworking line
- 112112
- LenkungsdruckwaageSteering pressure
- 114114
- LenksteuerleitungSteering control line
- 116116
- DruckwaagenfederCompensator spring
- 118118
- Steuerleitungcontrol line
- 120120
- Düsejet
- 122122
- Düsejet
- 124124
- Steuerkanalcontrol channel
- 126126
- weiteres Rückschlagventilanother check valve
- 128128
- DruckreduzierventilPressure reducing valve
- 130130
- Kanalchannel
Claims (15)
- A hydraulic control arrangement for a mobile machine comprising at least two hydraulic loads (10, 12, 14) which can be supplied with pressure fluid by a pump in response to the maximum load pressure, wherein the pressure fluid volume flow to one of the loads (10) for a lifting function and to a load (12, 14) actuating another function of the machine is defined via a respective inflow metering orifice (36, 44) and an LUDV pressure regulator (38, 46) allocated thereto, each of which is pressurized in the opening direction by the pressure downstream of the allocated inflow metering orifice (36, 44) and in the closing direction by pressure approximately corresponding to the maximum load pressure of the loads (10, 12, 14), characterized in that in a return line from the load (10) provided for lifting to the control of lowering an LS valve (50) an including LS metering orifice (52) and an LS pressure regulator (54) is arranged.
- The hydraulic control arrangement according to claim 1, wherein another load, for instance for tilting a boom, is controlled via a proportional valve.
- The hydraulic control arrangement according to claim 1, wherein an inflow metering orifice (36) and the pertinent LUDV pressure regulator (38) are allocated to at least two loads (12, 14).
- The hydraulic control arrangement according to claim 3, wherein a directional valve (30, 32) for adjusting the pressure fluid flow direction to and from the load (12, 14) is allocated to at least one of the loads (12, 14).
- The hydraulic control arrangement according to any one of the preceding claims, wherein the inflow metering orifice (36, 44) is formed by a continuously variable two-way valve.
- The hydraulic control arrangement according to any one of the claims 3 to 5, wherein a pressure relief valve (128) is provided downstream of the LUDV pressure regulator (38).
- The hydraulic control arrangement according to any one of the preceding claims, wherein downstream of the LUDV pressure regulator (46) of the load (10) provided for lifting, a check valve (84) opening toward the latter is disposed and a return passage (86) branches off between the check valve (84) and the load (10).
- The hydraulic control arrangement according to any one of the preceding claims, comprising a steering unit (120) which has an LS inflow metering orifice for the pressure fluid supply of an actuator (104) of the steering (102) and to which a steering pressure regulator (112) is allocated.
- The hydraulic control arrangement according to claim 8, wherein the steering pressure regulator (112) is pressurized in the closing direction by the pressure prevailing upstream of the LS inflow metering orifice of the steering unit (106) and in the opening direction by a spring (116) and the pressure prevailing in a control line (118, 130) connected to a line portion conducting a load pressure of the steering.
- The hydraulic control arrangement according to claim 9, wherein a line portion located downstream of the steering pressure regulator (112) is connected, via a control passage (124) and a check valve blocking in the direction of the steering unit (106), to an LS line (60) conducting the maximum load pressure of the loads (10, 12, 14).
- The hydraulic control arrangement according to claim 9, wherein the control line (118) leads from a pressure fluid flow path upstream of the steering pressure regulator (112) to a line portion conducting the load pressure of the steering, two nozzles (120, 122) being arranged in the control line (118), and in the area between the two nozzles (120, 122) a control passage (124) leading to a control chamber active in the opening direction of the steering pressure regulator (112) branches off which is connected to an LS line (60) conducting the maximum load pressure via a check valve (126).
- The hydraulic control arrangement according to any one of the preceding claims, wherein the pump is a constant displacement pump to which a bypass pressure regulator (58) is allocated which is pressurized in the opening direction by the pump pressure and in the closing direction by the maximum load pressure prevailing in the LS line (60) and a pressure regulator spring.
- The hydraulic control arrangement according to claim 8 or 9, wherein the LS line (60) is connected to a tank via a relief valve (62).
- The hydraulic control arrangement according to any one of claims 8, 9 or 11, wherein the pressure prevailing in the LS line (60) is limited via an LS pressure limiting valve (66).
- The hydraulic control arrangement according to any one of the preceding claims, wherein the mobile machine is a forklift, with a lifting cylinder (10) for lifting a load, a tilting cylinder (12) for tilting and a displacement cylinder (14) for laterally displacing a boom being provided, wherein a common LUDV valve (34) is preferably associated to the two latter loads.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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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 |
Publications (2)
Publication Number | Publication Date |
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EP2142808A1 EP2142808A1 (en) | 2010-01-13 |
EP2142808B1 true EP2142808B1 (en) | 2012-02-08 |
Family
ID=39719645
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08734422A Not-in-force EP2142808B1 (en) | 2007-03-27 | 2008-03-20 | Hydraulic control arrangement |
Country Status (5)
Country | Link |
---|---|
US (1) | US8915075B2 (en) |
EP (1) | EP2142808B1 (en) |
AT (1) | ATE544954T1 (en) |
DE (1) | DE102007028864A1 (en) |
WO (1) | WO2008116451A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012203386A1 (en) * | 2012-03-05 | 2013-09-05 | Robert Bosch Gmbh | control arrangement |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011103868A1 (en) | 2011-06-10 | 2012-12-13 | Robert Bosch Gmbh | Hydraulic drive for mobile working machine, has low-pressure feed line, which connects hydraulic accumulator to port of hydraulic machine, where accumulator discharge valve unit is arranged |
JP5860711B2 (en) * | 2012-02-03 | 2016-02-16 | Kyb株式会社 | Fluid pressure control device |
DE102012208944A1 (en) * | 2012-05-29 | 2013-12-05 | Robert Bosch Gmbh | Hydrostatic valve assembly and hydrostatic control assembly with the valve assembly |
JP5948260B2 (en) * | 2013-01-24 | 2016-07-06 | Kyb株式会社 | Fluid pressure control device |
US20140277697A1 (en) * | 2013-03-15 | 2014-09-18 | Raymond Francis McDonald | Transport system with at least one position sensor |
CN107191441A (en) * | 2017-07-27 | 2017-09-22 | 徐州重型机械有限公司 | Hydraulic system, the control method of hydraulic system and engineering machinery |
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DE3321483A1 (en) * | 1983-06-14 | 1984-12-20 | Linde Ag, 6200 Wiesbaden | HYDRAULIC DEVICE WITH ONE PUMP AND AT LEAST TWO OF THESE INACTED CONSUMERS OF HYDRAULIC ENERGY |
US5115720A (en) * | 1990-04-02 | 1992-05-26 | Baker Material Handling Corporation | Hydraulic valve bank |
DE69132071T2 (en) * | 1990-05-15 | 2000-11-16 | Komatsu Mfg Co Ltd | Hydraulic system |
DE9106442U1 (en) | 1991-05-25 | 1991-08-14 | Buchholz Hydraulik GmbH, 24147 Klausdorf | Control for hydraulic consumers |
DE9317308U1 (en) * | 1993-11-11 | 1995-03-16 | Brugger, Klaus, Dipl.-Ing., 83700 Rottach-Egern | Hydraulic system for the hydraulic actuation of an ambulance lifting table |
DE4341244C2 (en) * | 1993-12-03 | 1997-08-14 | Orenstein & Koppel Ag | Control for dividing the flow rate made available by at least one pump in hydraulic systems among several consumers |
DE4434532A1 (en) * | 1994-02-25 | 1995-08-31 | Danfoss As | Hydraulic steering system for work vehicles |
DE4417962A1 (en) * | 1994-05-21 | 1995-11-23 | Rexroth Mannesmann Gmbh | Control arrangement for at least two hydraulic consumers |
DE19703997A1 (en) * | 1997-02-04 | 1998-08-06 | Mannesmann Rexroth Ag | Hydraulic control circuit for a priority and for a subordinate hydraulic consumer |
DE19828963A1 (en) * | 1998-06-29 | 1999-12-30 | Mannesmann Rexroth Ag | Hydraulic switch system for the operation of low- and high-load units |
DE19904616A1 (en) * | 1999-02-05 | 2000-08-10 | Mannesmann Rexroth Ag | Control arrangement for at least two hydraulic consumers and pressure differential valve therefor |
KR20010071204A (en) * | 1999-03-04 | 2001-07-28 | 세구치 류이치 | Hydraulic circuit device |
KR100379863B1 (en) * | 1999-04-26 | 2003-04-11 | 히다치 겡키 가부시키 가이샤 | Hydraulic circuit system |
US6293099B1 (en) | 1999-06-28 | 2001-09-25 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Hydraulic circuit for forklift |
DE19937224A1 (en) * | 1999-08-06 | 2001-02-08 | Mannesmann Rexroth Ag | Hydraulic control arrangement for the demand-flow-controlled (load-sensing-regulated) pressure medium supply of preferably several hydraulic consumers |
DE10119276B4 (en) | 2001-04-20 | 2009-12-10 | Bosch Rexroth Aktiengesellschaft | Hydraulic control circuit |
DE20208577U1 (en) * | 2002-06-03 | 2003-12-11 | Hawe Hydraulik Gmbh & Co. Kg | Electro-hydraulic lift control device for industrial trucks |
EP1576241B1 (en) * | 2002-12-18 | 2007-06-13 | Bosch Rexroth AG | Control device for a work device comprising a scoop held on an extension arm |
DE10325295A1 (en) * | 2003-06-04 | 2004-12-23 | Bosch Rexroth Ag | Hydraulic control arrangement |
DE10332120A1 (en) * | 2003-07-15 | 2005-02-03 | Bosch Rexroth Ag | Control arrangement and method for controlling at least two hydraulic consumers |
US6931847B1 (en) * | 2004-03-04 | 2005-08-23 | Sauer-Danfoss, Inc. | Flow sharing priority circuit for open circuit systems with several actuators per pump |
DE102004011913B4 (en) * | 2004-03-11 | 2005-12-29 | Jungheinrich Ag | Hydraulic lifting device for battery-operated industrial trucks |
US7600612B2 (en) * | 2005-04-14 | 2009-10-13 | Nmhg Oregon, Llc | Hydraulic system for an industrial vehicle |
GB0603991D0 (en) * | 2006-02-28 | 2006-04-05 | Agco Gmbh | Hydraulic systems for utility vehicles, in particular agricultural vehicles |
-
2007
- 2007-06-22 DE DE102007028864A patent/DE102007028864A1/en not_active Withdrawn
-
2008
- 2008-03-20 AT AT08734422T patent/ATE544954T1/en active
- 2008-03-20 EP EP08734422A patent/EP2142808B1/en not_active Not-in-force
- 2008-03-20 US US12/532,973 patent/US8915075B2/en not_active Expired - Fee Related
- 2008-03-20 WO PCT/DE2008/000491 patent/WO2008116451A1/en active Application Filing
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012203386A1 (en) * | 2012-03-05 | 2013-09-05 | Robert Bosch Gmbh | control arrangement |
Also Published As
Publication number | Publication date |
---|---|
US8915075B2 (en) | 2014-12-23 |
DE102007028864A1 (en) | 2008-10-02 |
US20100212308A1 (en) | 2010-08-26 |
EP2142808A1 (en) | 2010-01-13 |
ATE544954T1 (en) | 2012-02-15 |
WO2008116451A1 (en) | 2008-10-02 |
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