CN105840566A - Hydraulic control device for supplying pressure medium to at least two hydraulic loads - Google Patents
Hydraulic control device for supplying pressure medium to at least two hydraulic loads Download PDFInfo
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- CN105840566A CN105840566A CN201610269885.4A CN201610269885A CN105840566A CN 105840566 A CN105840566 A CN 105840566A CN 201610269885 A CN201610269885 A CN 201610269885A CN 105840566 A CN105840566 A CN 105840566A
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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
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
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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
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
- F15B19/007—Simulation or modelling
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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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
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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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/25—Pressure control functions
- F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
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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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
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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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
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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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
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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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
The invention relates to a hydraulic control device for supplying a pressure medium to at least two hydraulic loads. The hydraulic control device is provided with a hydraulic pump with an adjustable work volume. The adjustment of hydraulic pump is changed by a pump regulator according to the highest load pressure of the actuated hydraulic load: the pump pressure exceeds a pump pressure than the highest load pressure of simultaneously controlled hydraulic load. At least two valve arrangements are provided, each valve arrangement comprises an orifice plate and an individual pressure maintaining valve arranged in series with the metering orifice, a first valve arrangement is arranged between a pump line leading from the hydraulic pump and a first hydraulic load, a second valve arrangement is arranged between the pump line and a second hydraulic load. The pump controller is controlled in such a way that different pressure drops in the pump line are taken into account at the level of the pump pressure difference, and individual pressure maintaining valve is at least almost completely opened in the case of different pressure drops in the pump line.
Description
Technical field
The present invention relates to a kind of for the hydraulic control device at least two hydraulic load supply pressure medium, having at its swept volume (Hubvolumen) aspect adjustable hydrostatic pump, its regulation is changed by pump control mechanism in the following manner according to the maximum load pressure of the hydraulic load handled: pump pressure exceedes one the pump pressure difference of maximum load pressure of the hydraulic load simultaneously manipulated.There is at least two valve gear, each of which valve gear all includes the single pressure retaining valve (Individualdruckwaage) measuring orifice plate (Zumessblende) and being arranged in rows with metering orifice plate, and wherein the first valve gear is arranged in the pump conduit by hydraulic pump and between the first hydraulic load, and the second valve gear is arranged between pump conduit and the second hydraulic load, because pump pressure is adjusted according to maximum load pressure, therefore such hydraulic control device is also known as according to load sensing or the control device of load-transducing principle.Hereinafter such control device is referred to as LS-and controls device.
Background technology
Such as, device is controlled from the known one of DE 197 14 141 A1 such hydraulic pressure LS.Controlling in device at this known hydraulic pressure LS-, the pressure retaining valve being arranged in rows with metering orifice plate and is loaded by spring along opening direction by the corresponding pressure measuring orifice plate downstream, and along closing direction by the pressure-loaded of this metering orifice plate upstream.Generally this pressure retaining valve is arranged in the upstream of metering orifice plate, so that the pressure in metering orifice plate downstream is the load pressure of corresponding hydraulic load.
In other kinds of hydraulic pressure LS-controls device, pressure retaining valve is arranged in after metering orifice plate, and along opening direction by the pressure-loaded measured accordingly after orifice plate, and along closedown direction by being in the control pressure-loaded controlling intracavity, this control pressure generally corresponds to the maximum load pressure of all hydraulic load supplied by same hydraulic pump.If measuring orifice plate when handling multiple hydraulic load at the same time and opening the most big, make by being adjusted until the pressure medium amount that the hydraulic pump of retainer provides is less than the pressure medium amount of general requirement, then the pressure medium amount flowing into each hydraulic load reduces identically with the corresponding load pressure independently ratio of hydraulic load.Thus, a kind of hydraulic control device with the flow distribution device (LUDV-control device) unrelated with load pressure of touching upon.Even if because also the highest load pressure is arrived in detection (abf ü hlen) in the case of LUDV-controls device, and produced the pump pressure exceeding certain pressure differential than maximum load pressure by hydraulic pump, so it is the special case that LS-controls device that LUDV-controls device.
The volume flow carried by hydraulic pump in known LS-controls device so adjusts so that obtain exceeding, than maximum load pressure, the pump pressure that constant pump pressure is poor at pump discharge.Typical pump pressure difference for example, 22 bar.But for the load-transducing amount for being carried out by metering orifice plate is regulated, typically needing to exceed only 10 bars than it, they are adjusted by these pressure retaining valves having in the Loadsensing control device of the metering orifice plate upstream and downstream single pressure retaining valve that is loaded pressure.Remaining 12 bar of so-called overvoltage and volume flow about the pressure drop that is divided in pump conduit and by distributing to the unwanted pressure drop of pressure retaining valve of the highest hydraulic load of load pressure itself.The most so select this overvoltage so that in the case of maximum volume flow and/or in the case of disadvantageous volume flow is distributed, each metering orifice plate still has desired pressure differential available.Otherwise it means that in the case of the pressure drop associated little volume flow little with in pump conduit and/or under favourable volume flow distribution condition, the pressure retaining valve distributing to the highest hydraulic load of load pressure suppresses whole overvoltage.Then, the pressure retaining valve distributing to that other handle simultaneously and that load pressure is relatively low hydraulic load the stress level the increased suppression from the input of respective valve device must add the pressure differential on this metering orifice plate to a pressure, this pressure equal to relatively low load pressure.
Summary of the invention
The task of the present invention is, it is provided that a kind of LS-controls device, and this LS-controls device and has higher energy efficiency when only having little change relative to known LS-control device.
This task is solved by a kind of hydraulic control device, this hydraulic control device has adjustable hydrostatic pump in terms of its swept volume, and its regulation is changed by pump control mechanism in the following manner according to the maximum load pressure of the hydraulic load handled: pump pressure exceedes one the pump pressure difference of maximum load pressure of the hydraulic load simultaneously manipulated；And there is at least two valve gear, each of which valve gear all includes the single pressure retaining valve measuring orifice plate and being arranged in rows with metering orifice plate, and wherein the first valve gear is arranged in the pump conduit by hydraulic pump and between the first hydraulic load, and the second valve gear is arranged between pump conduit and the second hydraulic load.According to the present invention, manipulate described pump control mechanism in the following manner: the different pressure drop considering in this pump conduit on the height of this pump pressure difference, and the most almost fully open in the case of distributing to the single pressure retaining valve of the highest hydraulic load of the load pressure different pressures fall in this pump conduit.If the hydraulic load that the most only manipulation one is uniquely supplied by this pump, then this hydraulic load is exactly naturally also the hydraulic load that load pressure is the highest.
Then the basic thought of the present invention is, overvoltage is correspondingly matched with until the intended pressure drop of corresponding measurement orifice plate, thus the pressure drop in the suppression carried out by distributing to the pressure retaining valve of the highest hydraulic load of load pressure, i.e. this single pressure retaining valve is the least.Then, the pressure drop distributed on the pressure retaining valve of other hydraulic load simultaneously manipulated the most correspondingly reduces, thus obtains higher energy efficiency.
The scheme that is advantageously improved of the hydraulic control device according to the present invention can be drawn by dependent claims.
The present invention is realized in a particularly advantageous manner for LS-controls device, the single pressure retaining valve of at least two of which is along cutting out direction by measuring the pressure-loaded of orifice plate upstream accordingly, and along opening direction by measuring the pressure in orifice plate downstream accordingly and being loaded by regulation spring.Then the LUDV-being not related to have the flow distribution device relevant with load pressure at this controls device, and the LS-relating to routine controls device, wherein when under-supply, the hydraulic load that load pressure is the highest is not reentried desired pressure medium amount, and it becomes the slowest compared with the hydraulic load that load pressure is less.Even if but the present invention still can be advantageously employed in the case of LUDV-controls device, because the pressure medium amount flowing through this metering orifice plate in the case of certain open cross-section of metering orifice plate can be accomplished unrelated with the pressure drop in this pump conduit.
Pressure drop in this pump conduit depends primarily on the volume flow flow through.Thus the rotating speed of this hydraulic pump and the swept volume of this hydraulic pump may be detected by sensor, the volume flow in this pump conduit is obtained by means of this rotating speed and swept volume, and it is poor to adjust described pump pressure according to volume flow, and it is responsible for by this way making the pressure on the input of valve gear corresponding to desired pressure, thus the single pressure retaining valve of the highest hydraulic load of load pressure does not suppresses or suppresses the most on a small quantity, or determine the pressure differential on this metering orifice plate in the case of LUDV-controls device.
From the characteristic curve stored, advantageously take out described pump pressure poor, described characteristic curve stores the numerical value that the pump pressure relevant with volume flow is poor.As an alternative, this pump pressure can be calculated on-line manner in the case of considering physical relation and parameter poor.
Generally adjustable pump is used in LS-and controls in device, it is assigned with regulation valve as pump control mechanism for described pump, described regulation valve is loaded by pump pressure in the case of the swept volume of hydraulic pump reduces, and by maximum load pressure and is especially loaded by regulation spring in the case of the swept volume of hydraulic pump increases.This pump pressure difference can change the most in the following manner now: this regulation valve additionally can be loaded by the electric executive component manipulated towards an action direction in two action directions.If this executive component utilizes pump pressure to work, then this pump pressure difference is the least, this executive component the power applied is the biggest.If this executive component works against pump pressure, then this pump pressure difference is the biggest, this executive component the power applied is the biggest.Advantage in this design essentially consists in, and compared with known system, when executive component is out of order, this system works in the case of not having function to limit.
Also it is possible that described maximum load pressure is detected by electric pressure sensor, and by the maximum load pressure detected, volume flow and distribute to the pump pressure difference of this volume flow to obtain pump pressure.Described hydraulic pump can be carried out pressure regulation subsequently, and this hydraulic pump has the pump control mechanism of energy electricity manipulation, and calculated pump pressure wherein flows to as pump pressure rated value the pump control mechanism of described hydraulic pump.Advantageously, described pump pressure rated value is flowed to described pump control mechanism after filtering.If this pump control mechanism also has the regulation spring worked on pump control mechanism against pump pressure, then this pump pressure rated value is than the pressure equivalent of described pump pressure rated value minor adjustment spring.
Additionally, here it is advantageous when, it is possible to use the actuator of electronization carrys out requirement pump pressure, without the rated pressure signal producing hydraulic pressure.In some cases, save and lead to the hydraulic control circuit of hydraulic pump.In multiple hydraulic load with multiple pressure transducer, each pressure query can be evaluated and determine priority.Reversal valve or the check-valves for selecting maximum load pressure can be saved in the case of multiple hydraulic load.
Advantageously, there is temperature sensor, wherein by the viscosity of temperature anti-pushing force medium, and it is poor wherein to regulate described pump pressure in the case of the viscosity considering this pressure medium.
It is also advantageous that there is pressure transducer, know the pressure differential on a metering orifice plate or multiple metering orifice plate by means of described pressure transducer.Thus can identify the actual pressure drop occurred in machine, and in some cases it is adjusted.This is mainly favourable in LUDV-controls device.
Finally can by other parameters such as: the position of volume flow rated value, volume flow actual value, metering orifice plate or pressure retaining valve combines in the calculating that pressure information is dissolved into described pump pressure difference.
Two embodiments of the hydraulic control device according to the present invention shown in the drawings.Now according to these accompanying drawings, the present invention is described in greater detail.
Accompanying drawing explanation
In accompanying drawing:
Fig. 1 shows first embodiment, is wherein added in by variable magnetic force on pump control mechanism in the power applied by maximum load pressure and spring；And
Fig. 2 shows the second embodiment, is wherein added in the power applied by spring by variable magnetic force on pump control mechanism, described magnetic force corresponding to maximum load pressure and pump pressure difference variable share add and.
Detailed description of the invention
Shown hydraulic control device is that the LS-with multiple valve gear controls device, shows two valve gears 10 and 11 the most in these figures.Generally multiple valve gears are assembled into control block with integral blocks or in disc structure mode.In terms of direction and speed, the hydraulic load 12 being configured to hydraulic differential cylinder can be controlled by valve gear 10, and the hydraulic load 13 being likewise constructed to differential cylinder can be controlled by valve gear 11.
To this end, valve gear 10 has metering orifice plate 14, this metering orifice plate is commonly constructed on the control piston only schematically illustrated as rectangle, and its open cross-section determines the pressure medium amount flowing into hydraulic load 12.Additionally, be constructed so as to described control piston so that utilize this control piston to select, the pressure medium amount flowing through metering orifice plate 14 flows into which cylinder chamber of differential cylinder 12, and pressure medium is extruded and flows out to fuel tank 15 from which cylinder chamber.Which cylinder chamber pressure medium flows into selects the downstream at metering orifice plate 14 to carry out, thus measures orifice plate 14 in principle and be just enough to be used in the two cylinder chamber of this differential cylinder.But, it being usually present two metering orifice plates, they are arranged between two control chambeies of this valve gear, and wherein make one of them or another metering orifice plate work depending on controlling the steering of piston.
Controlling piston-metering orifice plate 14 to be positioned on this control piston-can adjust continuously from centre position to two contrary directions, wherein along with the increase of regulation (degree), the open cross-section of metering orifice plate 14 becomes increasing.
The single pressure retaining valve 16 of upstream arrangement at metering orifice plate 14, this single pressure retaining valve is to have adjustable choke valve flowing through cross section, its flow check piston not being shown specifically by the pressure in metering orifice plate 14 downstream and is loaded by regulation spring in the case of open cross-section increases, and by the pressure-loaded of metering orifice plate 14 upstream in the case of open cross-section reduces.This pressure retaining valve manipulates by the holding of this metering orifice plate corresponding to regulating the pressure differential of the pressure equivalent of spring according to described.Currently such as it is desirable to 10 bars.
Corresponding with valve gear 10, valve gear 11 has metering orifice plate 24, and this metering orifice plate is commonly constructed on the control piston only schematically illustrated as rectangle, and its open cross-section determines the pressure medium amount flowing into hydraulic load 13.Additionally, be constructed so as to described control piston so that utilize this control piston to select, the pressure medium amount flowing through metering orifice plate flows into which cylinder chamber of differential cylinder 13, and pressure medium is extruded and flows out to fuel tank 15 from which cylinder chamber.Which cylinder chamber pressure medium flows into selects the downstream at metering orifice plate 24 to carry out, thus measures orifice plate 24 in principle and be just enough to be used in the two cylinder chamber of this differential cylinder 13.But, it being usually present two metering orifice plates, they are arranged between two control chambeies of this valve gear, and wherein make one of them or another metering orifice plate work depending on controlling the steering of piston.
Controlling piston-metering orifice plate 24 to be positioned on this control piston-can adjust continuously from centre position to two contrary directions, wherein along with the increase of regulation (degree), the open cross-section of metering orifice plate 24 becomes increasing.The single pressure retaining valve 26 of upstream arrangement at metering orifice plate 24, this single pressure retaining valve is to have adjustable choke valve flowing through cross section, its flow check piston not being shown specifically by the pressure in metering orifice plate 24 downstream and is loaded by regulation spring in the case of open cross-section increases, and by the pressure-loaded of metering orifice plate 24 upstream in the case of open cross-section reduces.This pressure retaining valve manipulates by the holding of this metering orifice plate corresponding to regulating the pressure differential of the pressure equivalent of spring according to described.Currently such as it is desirable to 10 bars.As the same with single pressure retaining valve 16 in view of metering orifice plate 14, the most such as, want 10 bars.
The two differential cylinder 12 and 13 is provided pressure medium by a unique hydraulic pump 30.Hydraulic pump 13 is adjustable in terms of its swept volume, and wherein said swept volume is the pressure medium amount carried by this hydraulic pump when the drive shaft of hydraulic pump rotates.Conveying capacity or the volume flow produced by this hydraulic pump by instantaneous swept volume and drive the rotating speed of hydraulic pump to draw.
Hydraulic pump 30 regulates valve 31 equipped with load-transducing, and this load-transducing regulation valve is typically mounted on pump object, and has the first joint, and this first joint is connected with the regulation chamber fluid adjacent with the regulating piston of hydraulic pump (Stellkolben).Second joint of regulation valve 31 is connected with the compression fittings fluid of this hydraulic pump.Finally, the 3rd joint is connected with fuel tank.This regulation valve has adjustment piston (Regelkolben), utilizes this adjustment piston can control the pressure medium flow path between these three joint.The direction that adjustment piston connects along the first joint and the second joint is applied in pump pressure on the first plane, and it is applied in a power along the direction that the first joint and the 3rd joint connect, this power is equal to the power produced in the second plane being equivalent to the first plane in terms of its size by maximum load pressure, load additionally, be also conditioned spring 32.The pressure equivalent of regulation spring 32 is such as equal to 12 bars.If the power applied by pump pressure exceedes counteracting force, then this regulation chamber is connected with the compression fittings of hydraulic pump.Thus, pressure medium flows into regulation chamber, so that the swept volume of this hydraulic pump reduces.If the power applied by pump pressure is less than counteracting force, then this regulation chamber is connected with fuel tank.The most such as can clamp-on fuel tank by the spring handle pressure medium that regulating piston is loaded from this regulation chamber, so that the swept volume of this hydraulic pump increases.
Hydraulic pump 30 is connected with valve gear 10 and 11 fluid by pump conduit 33.
The maximum load pressure of all hydraulic load simultaneously handled is selected by reversal valve 34, and according to the embodiment of Fig. 1, it is notified to this regulation valve 31 by load circular pipeline (Lastmeldeleitung) 35, and according to the embodiment of Fig. 2, is notified to pressure transducer 39.
In the case of not having further measure, the pump pressure difference between pump pressure and maximum load pressure is constant, and the pressure equivalent of the regulation spring 32 corresponding to regulation valve 31.At this, pump pressure difference can so set, although making the pressure differential distributing on the metering orifice plate of the highest hydraulic load of instantaneous load pressure at pump conduit until having pressure drop in corresponding single pressure retaining valve, the most not dropping below relevant single pressure retaining valve and making every effort to the numerical value of regulation.Pressure drop in pump conduit increases along with the volume flow flowing through this pipeline, and maximum when this volume flow maximum.If then this pressure drop for example, 12 bar, then pump pressure necessarily be greater than maximum load pressure 22 bar, in order to ensures to still suffer from the pressure differential of 10 bars on the metering orifice plate of the highest hydraulic load of load pressure.Then, 12 bars are so-called overvoltages.
But on the other hand this mean, when less in volume flow and in pump conduit 33 pressure drop is less, single pressure retaining valve now has in the way of the pressure deducting in pump conduit than overvoltage reduces a numerical value suppress pump pressure, wherein this point is also applied for the single pressure retaining valve of the relatively low hydraulic load of the load pressure simultaneously handled, and described single pressure retaining valve the most after all must suppress pump pressure.
According in the embodiment of Fig. 1, the direction that the regulating piston of regulation valve 31 connects along the first joint and the second joint is applied in pump pressure on the first plane, and in terms of its size, maximum load pressure is equivalent to apply in the second plane of the first plane along the direction that the first joint and the 3rd joint connect, and load additionally, be also conditioned spring 32.
In order to can relatively efficiently configuration energy input, the regulating piston of regulation valve 31 is also loaded by the adjustable electric magnet of ratio 36 along the direction that the second joint and the 3rd joint connect in addition to maximum load pressure and regulation spring 32 in this first embodiment.This electric magnet controls according to the volume flow in pump conduit 33.
In order to obtain volume flow, speed probe 40 detect the rotating speed driving hydraulic pump 30.The swept volume of hydraulic pump is detected by position sensor 41, and this position sensor such as detects the position of the regulating piston of pump.Then, described volume flow is multiplied by rotating speed by swept volume and is given, and if it is intended to it is very accurate, is then multiplied by the volume coefficient of efficiency of hydraulic pump in electronic control unit 42.Obtain now according to the characteristic curve 43 stored, which pump pressure is paid close attention to poor for this, make in the case of the volume flow of hydraulic pump 30 is given, pressure on the input of single pressure retaining valve distributing to the highest hydraulic load of load pressure is the highest so that single pressure retaining valve must suppress the least pressure.Desirably this pressure is in more than load pressure just 10 bar.
Electric magnet 36 is manipulated now according to calculated pump pressure difference.If this volume flow is less, the least pump pressure difference such as 12 bar or the least enough.The regulation spring 32 of regulation valve 31 should adjust on the pressure equivalent of 12 bars, thus does not manipulates electric magnet 36 when observed volume flow is less.If it is determined that this instantaneous volume flow requires that the pump pressure of such as 16 bars is poor, then electric magnet 36 is energized in the following manner: in addition to regulation spring 32, this electric magnet also produces the power being equivalent to 4 bar pressures.Therefore, pump pressure rises to 16 bars.Correspondingly in the case of other volume flows, this electric magnet is manipulated.
Electric magnet can also be applied to regulate on the regulating piston of valve 31 in the sense that identical with pump pressure.Then, this regulation spring must have the pressure equivalent of 22 bars.Then, this electric magnet can be energized when volume flow is less, in order to produces the pump pressure being in more than maximum load pressure only 10 to 12 bar.This electric magnet is not manipulated when volume flow is the biggest, thus pump pressure exceedes maximum load pressure with the pressure equivalent regulating spring for amplitude.
According in the embodiment of Fig. 2, as obtaining the volume flow of hydraulic pump 30 according to the embodiment of Fig. 1.Obtain also according to the characteristic curve 43 stored that to pay close attention to which pump pressure for this poor, make in the case of the volume flow of hydraulic pump 30 is given, pressure on the input of single pressure retaining valve distributing to the highest hydraulic load of load pressure is the highest so that single pressure retaining valve must suppress the least pressure.
According in the embodiment of Fig. 2, signal can also be filtered being delivered to summing junction 45 in this analysis circuit by the maximum load pressure detected by pressure transducer 39 by analysis circuit 44, the signal that would correspond to pressure differential in this summing junction is added on the signal of telecommunication corresponding with the highest load pressure, in order in the case of volume flow is given, this pump pressure difference should exceed the pressure equivalent of regulation spring 32.The adjustable electric magnet of numerical value comparative example 46 according to being added manipulates.This electric magnet different from the electric magnet 36 of the embodiment according to Fig. 1 only apply such a power, this power be added to regulate in the power of spring 32 and be added to the power of the electric magnet 46 of the embodiment in the power that produced by maximum load pressure according to Fig. 2 corresponding to the power that produced by maximum load pressure and a power add and, this power is required, in order to obtain desired pump pressure in the case of volume flow is given together with the power applied by this regulation spring 32 poor.
This maximum load pressure such as should be equal to 180 bars.If this volume flow is less, the least pump pressure difference such as 12 bar or the least enough.The regulation spring 32 of regulation valve 31 to be also adjusted on the pressure equivalent of 12 bars in the case of according to Fig. 2 embodiment, thus so manipulating described electric magnet 46 when observed volume flow is less so that the power being applied to regulate on the regulating piston of valve 31 by this electric magnet is corresponding to the load pressure of 180 bars.If it is determined that the pump pressure that instantaneous volume flow requires such as 16 bars is poor, then electric magnet 46 is energized in the following manner: the power applied by this electric magnet, corresponding to the power of 184 bars, i.e. adds 4 bars required for drawing the pump pressure difference of 16 bars together with 12 bars of regulation spring 32 corresponding to maximum load pressure.
Reference numerals list:
10 valve gears
11 valve gears
12 differential cylinders
13 differential cylinders
14 metering orifice plates
15 fuel tanks
16 single pressure retaining valves
24 metering orifice plates
26 single pressure retaining valves
30 hydraulic pumps
31 load-transducing regulation valves
32 regulation springs
33 pump conduit
34 reversal valves
35 load circular pipelines
36 electric magnet
39 pressure transducers
40 speed probes
41 position sensors
42 electronic control units
43 characteristic curves
44 analysis circuit
45 summing junctions
46 electric magnet.
Claims (11)
1. for the hydraulic control device at least two hydraulic load (12,13) supply pressure medium, tool
Have adjustable hydrostatic pump (30) in terms of its swept volume, its regulation according to handled hydraulic load (12,
13) maximum load pressure is changed in the following manner by pump control mechanism (31): pump pressure exceedes simultaneously
One pump pressure difference of maximum load pressure of the hydraulic load (12,13) of manipulation,
There is at least two valve gear (10,11), each of which valve gear all include measure orifice plate (14,
24) the single pressure retaining valve (16,26) and with this metering orifice plate (14,24) being arranged in rows, and
Between wherein the first valve gear is arranged in by pump conduit (33) and the first hydraulic load this hydraulic pump,
And the second valve gear is arranged between this pump conduit (33) and the second hydraulic load,
It is characterized in that, manipulate described pump control mechanism (31) in the following manner: at the height of this pump pressure difference
Different pressure drop in the described pump conduit of upper consideration (33), and distribute to the hydraulic pressure that load pressure is the highest
In the case of the single pressure retaining valve (16,26) of load (12,13) different pressures fall in this pump conduit
The most almost fully open.
2. according to the hydraulic control device described in claim 1, the single pressure retaining valve of at least two of which (16,
26) along closing direction by measuring the pressure-loaded of orifice plate (14,24) upstream accordingly, and along opening
Direction is by measuring the pressure in orifice plate (14,24) downstream accordingly and being loaded by regulation spring.
3. according to the hydraulic control device described in claim 1 or 2, wherein presence sensor (40,41),
Detected rotating speed and the swept volume of hydraulic pump (30) of hydraulic pump (30) by described sensor, wherein borrow
Help described rotating speed and swept volume to obtain the volume flow in pump conduit (33), and wherein according to should
It is poor that volume flow regulates described pump pressure.
4., according to the hydraulic control device described in claim 3, wherein take out from the characteristic curve stored
Described pump pressure is poor, stores the numerical value that the pump pressure relevant with volume flow is poor in described characteristic curve.
5., according to the hydraulic control device described in claim 3, calculate described pump pressure the most on-line manner
The numerical value of power difference.
6. according to the hydraulic control device described in the claims, wherein said pump control mechanism (31)
Be such a regulate valve, this regulation valve hydraulic pump (30) swept volume reduce in the case of by being pumped
Power manipulates, and by maximum load pressure and outstanding in the case of the swept volume of hydraulic pump (30) increases
It is manipulated by regulating spring, and this regulation valve can be attached towards an action direction in two action directions
Loaded by the executive component (36) that can electric manipulate with adding.
7. according to the hydraulic control device according to any one of claim 1 to 5, wherein said maximum load
Pressure is detected, wherein by the maximum load pressure detected, volume flow by electric pressure sensor (39)
Amount and distribute to the pump pressure difference of this volume flow to obtain pump pressure, wherein to described hydraulic pump (30)
Carry out pressure regulation, and this hydraulic pump has the pump control mechanism (31) of energy electricity manipulation, and wherein by institute
The pump pressure obtained flows to the pump control mechanism of described hydraulic pump (30) (31) as pump pressure rated value.
8. according to the hydraulic control device described in claim 7, wherein by described pump pressure rated value through filtering
Ripple flows to described pump control mechanism (31).
9., according to the hydraulic control device described in the claims, wherein there is temperature sensor, its
In by the viscosity of temperature anti-pushing force medium, and wherein adjust in the case of the viscosity considering this pressure medium
Save described pump pressure poor.
10., according to the hydraulic control device described in the claims, wherein there is pressure transducer, borrow
Help described pressure transducer and know the pressure differential on a metering orifice plate or multiple metering orifice plate.
11. according to the hydraulic control device described in the claims, wherein by other parameters such as: hold
The position of long-pending flow rated value, volume flow actual value, metering orifice plate or pressure retaining valve combines pressure information and incorporates
In the calculating of described pump pressure difference.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102015201318.9A DE102015201318A1 (en) | 2015-01-27 | 2015-01-27 | Hydraulic control arrangement for pressure medium supply at least two hydraulic consumers |
| DE102015201318.9 | 2015-01-27 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105840566A true CN105840566A (en) | 2016-08-10 |
| CN105840566B CN105840566B (en) | 2020-04-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610269885.4A Active CN105840566B (en) | 2015-01-27 | 2016-01-27 | Hydraulic control device for supplying at least two hydraulic consumers with a pressure medium |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN105840566B (en) |
| DE (1) | DE102015201318A1 (en) |
| IT (1) | ITUB20160407A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110088469A (en) * | 2016-12-22 | 2019-08-02 | 丹佛斯动力系统有限责任两合公司 | Manual displacement control device for axial poiston pump |
| CN112272725A (en) * | 2018-04-24 | 2021-01-26 | 普茨迈斯特工程有限公司 | Method and system for hydraulically controlling a cement dispensing boom |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102018206271A1 (en) | 2018-04-24 | 2019-10-24 | Putzmeister Engineering Gmbh | Method for controlling the movement of a mast and working machine |
| DE102021104398A1 (en) | 2021-02-24 | 2022-08-25 | Arburg Gmbh + Co Kg | Hydraulic device and method for controlling a hydraulic device |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN105840566B (en) | 2020-04-14 |
| DE102015201318A1 (en) | 2016-08-11 |
| ITUB20160407A1 (en) | 2017-07-26 |
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