Patent Application
20090145120
The invention relates to a method for the supply of pressure medium to at least two hydraulic consumers according to Claim 1 and to a circuit arrangement according to Claim 15.
In electronically implemented load-sensing (LS) systems for the supply of a plurality of hydraulic consumers, the energy efficiency can not only be improved by lowering the LS pressure difference. The control strategy can, furthermore, be modified such that the valve assigned to the currently highest loaded consumer is opened fully and the pump is regulated to a displacement, which, at the current rotational speed, satisfies the volume flow requirement of all the consumers. In the case of the further consumers, for example, an individual pressure balance then ensures that these do not consume more than the volume flow pertaining to them. Systems of this type are known from DE 103 40 993 A1 or EP 1 664 551 A1.
In the known systems, although it is possible to minimize energy losses, there is also nevertheless the disadvantage that the highest loaded consumer is controlled by the displacement of the variable-displacement pump. However, in comparison with valve controls, pump displacement controls have, relatively low dynamics, resulting in undesirable consequences. Thus, sudden fluctuations in the load pressure of the consumer subjected to the highest load can be smoothed out only inadequately. Moreover, load-pressure fluctuations of consumers subjected to lower load may penetrate to the pump side in spite of high-speed individual pressure balances. If these consumers have very low time constants, as is the case, for example, in motors with low mass inertia and short hydraulic lines, an influencing of the pump pressure then cannot be avoided entirely. In this case, too, the disturbance at the consumer subjected to the highest load can then be smoothed out only inadequately slowly by means of sluggish pump adjustment. Furthermore, the highest loaded consumer changes during operation. This means that, for all consumers which may possibly be at any one time the highest loaded consumer, two completely different control schemes are activated which use actuators of varying dynamics. This leads, at the operator, to a different feeling in the actuation of a consumer, depending on whether the consumer is or is not the highest loaded one.
The aim of the invention is to provide an improved supply of pressure medium to a plurality of consumers.
According to the invention, this is achieved by means of a method for controlling and regulating the supply of pressure medium to at least two hydraulic consumers, which are assigned in each case a directional valve for adjusting the flow and a source of a setpoint signal, and a pump with a variable displacement, which can be regulated by means of a displacement controller. The method comprises the method steps:
It is therefore proposed, in the system described in the introduction, to depart somewhat from the aim of maximum energy saving and not to open completely the valve belonging to the consumer having the highest load, but, instead, to open it only to a large extent. Fixing the operating point of the valve in this way below its full opening creates an, albeit minor, inflow pressure difference. The directional valve with its good dynamics is then available as an actuator and can compensate disturbances using the remaining residual opening. Setpoint changes, must, of course, continue to be compensated by the displacement control of the pump which also ensures the stationary accuracy of the volume flow.
It is advantageous if, in addition, maximum-pressure control is provided, which, when a preset pressure is reached, overrides the displacement control of the pump. The displacement is thereby set such that the maximum pressure is held, but is not overshot.
Preferably, a dynamic subcontroller is assigned to the consumer valve on the load side. At increasing pressure in the load line, its output is superposed additively to the valve signal in a way, that the spool position is increasing. Thus, sudden load changes will be compensated directly at the valve. If another dynamic subcontroller is added to the valve on the pump side, also pressure disturbances will be compensated which are caused by load changes at one of the other consumers. The output of this second subcontroller is superposed subtractively to the valve signal, so that the valve opening is decreasing when the pump pressure is rising. Thus the mutual influencing of various simultaneously operated consumers can be minimized. These dynamic subcontrollers preferably react to the rate of pressure change. If the pressure does not change or changes only slowly, the output signal from the subcontrollers is zero. Pressure peaks occurring generate an output signal which is superposed on that of the stationary-value control element of the valve control and which therefore smoothes out the pressure peaks directly at the directional valve. The dynamic subcontrollers are parameterizable and consequently adaptable to the individual time constants of different consumers.
The factor K for various consumers is to be dimensioned differently, dependent on their practical requirements. An optimal compromise between energy efficiency and dynamics can thereby be set. It is particularly advantageous if the factor K can be varied during the continuous operation of the appliance, so that changing requirements can be fulfilled during practical operation. Such adjustment may take place, for example, by hand or else automatically according to the current pressure level and/or the currently required volume flow. The system can consequently be designed adaptively since the controllers are designed identically for all consumers and no structural changes are required for different operating modes. The individual setting for the respective consumers occurs solely by varying the K value. This adaptation may likewise advantageously take place according to the current pump speed, the travel-drive control, the currently actuated consumers, the selected operating mode and/or the present oil temperature.
The invention relates, furthermore, to a circuit arrangement for controlling and regulating the supply of pressure medium to at least two hydraulic consumers, which are assigned in each case an electrically actuateable directional valve for flow control and a setpoint signal source. The circuit arrangement comprises also a pump with a displacement controller, adjusting the displacement according to the flow required by the setpoint signals of all consumers. The circuit comprises also a device for determining the consumer having the highest load and a control unit which controls the directional valve of the consumer having the highest load to a spool position y1. The spool position y1=K·y1,max=const. lies by a factor K, with 0<K<1, below the spool position y1,max representing the maximum opening of the directional valve. The circuit arrangement comprises also at least one dynamic subcontroller which is superposed on the control unit and smoothes out pressure fluctuations via the residual opening of the directional valve remaining between the valve-slide positions y1 and y1,max. By means of the dynamic subcontroller, sudden pressure fluctuations are not smoothed out at the pump, but only at the directional valve, while pump adjustment serves merely for virtually stationary supply as a function of the setpoint signals and the pump speed.
Further features and advantages of the invention may be gathered from the following figure description.
A pump P, driven for example by a diesel engine, not illustrated, rotates at the rotational speed nP. The pivot angle (and thus the displacement volume) of the pump P can be controlled via an electrically actuatable adjustment device VE. This regulation takes place by means of the displacement controller FVR according to the sum of the required flows QS011,1, and QS011,2 the displacement volume of the pump VP being regulated, taking into account the rotational speed of the pump nP, to
This setup allows to adjust flow and pressure in quasi-stationary operation according to the individual requirements of a plurality of consumers. Due to the inertia of the pump adjustment, however, rapid pressure fluctuations cannot be smoothed out satisfactorily. These pressure fluctuations occur frequently during the operation of the hydraulic consumers due to changing loads. For this purpose, the system according to the invention is provided at the directional valves V1, V2 of the individual consumers, because these directional valves can react far more quickly when pressure peaks occur.
First, in the figure, the control of the supply of the consumer Z2 having a lower load will be explained. A corresponding circuit of course must be provided for all consumers which, at any one time during operation, may not be the consumer subjected to the highest load. The flow Q2 to the consumer Z2 is obtained from the flow equation of the valve V2 as
Q
2=y2·C·√{square root over (pP−pzu,2)}
in which y2 is the spool position, C is a constant, pP is the pump pressure and Pzu,2 is the inflow-side pressure to the consumer Z2. Solving the equation for the spool position y2 yields the formula shown in the steady state controller SWS2. The output of the steady state controller SWS2 is based on the setpoint signal, and the pressure signals pP and Pzu,2 before and after the valve on the inflow path to consumer Z2.
In steady state, therefore, the valve spool position is predetermined and is fixed unequivocally. It remains unchanged as long as the steady state situation does not change. The steady state controller SWS2cannot act in the manner of a closed loop controller, it cannot process any difference between setpoint value and actual value and it also is not parameterizable.
To smooth out rapid pressure fluctuations, the dynamic subcontrollers DTRpzu,2 and DTRPp,2 are provided. They can react to pressure fluctuations on the load or pump side and by quickly changing the valve spool position, typically within less than ls, they can consequently improve the dynamic behaviour of the supply. These dynamic subcontrollers are designed in the exemplary embodiment of the figure as DT1-elements. They react to the rate of pressure change. Their outputs are zero when the pressure no longer changes or changes only slowly. In the event of a rapid pressure rise on the load side, which cannot be compensated by the steady state controller SWS2 nor by the displacement controller FVR, the signal of the dynamic subcontroller DTRpzu,2 is added to the signal of the steady state controller SWS2 and thereby is superposed on the control of the valve spool position y2 with the effect of enlarging the valve opening.
The situation is the opposite on the pump side. Here, above all, the mutual influencing of the consumers is to be avoided. Here, an instantaneous pressure rise leads to the valve opening being reduced, and therefore the signal of the pump-side dynamic subcontroller DTRp,2 is superposed subtractively on the control by the steady state controller SWS2. In the case of sudden pressure drops, of course, the behaviour is the opposite in both instances.
The described combination of the additive superposition of the load-side subcontroller and subtractive superposition of the pump-side subcontroller may also advantageously be reversed in specific instances. If, for example, the inlet metering edge is opened very wide, a penetration of a load-side disturbance to the pump side is in any case not entirely avoidable. In this case, it would be advantageous if the load-side subcontroller already acts subtractively and consequently initiates the reaction which is in any case caused shortly thereafter by the pump-side subcontroller.
An additive superposition of the pump-side subcontroller may, under certain circumstances, also make sense, for example when the hydraulic flexibility of the pump line is much greater than that of the load line. This may be the case in working machines which have a work platform rotatable against the undercarriage. Here, often, the drive assembly, including the pump, is located in the undercarriage and the valves in the platform. This helps to keep the number of lines low, which need to be led through the rotational joint. In a system of this type, pressure changes in the compliant pump line would cause far more vigorous reactions in the comparatively rigid load line. It may make sense here, according to the abovementioned strategy, to initiate at an early stage on the pump side the reaction which is in any case caused a short time later on the load side.
For the highest loaded consumer Z1, the control of the directional valve V1 takes place by means of the steady state controller SWS1, whose signal is superposed by the signal of the dynamic subcontrollers DTRpzu,1 and DTRPp,1, as described above. According to the invention, however, in this case the directional valve V1 does not open according to the required Qdes,1, but, instead, is opened to a fixed value which forms the operating point of the valve. The valve spool, although opening substantially, nevertheless remains below the maximum by a factor K. The valve-spool position y1 is accordingly determined as
y
1
=K·y
1.max
with
0<K<
where y1.max represents the maximum opening of the directional valve V1 of the consumer Z1 having the highest load.
Thus, between y1 and the maximum opening y1.max, a residual opening remains which according to the present invention is utilized for smoothing out rapid pressure fluctuations. Consequently, also in the case of the consumer Z1 having the highest load, the dynamic subcontrollers DTRpzu,1 and DTRPp,1 may be permanently active.
The relevant consumers Z1, Z2, etc. may not necessarily be synchronous cylinders, as illustrated in
The selection of the factor K is explained below by means of some examples:
The system behaviour may be set continuously between “high efficiency with poor dynamics” and “low efficiency with good dynamics”. The factor K alone serves for setting. The overall controller structure and parameterization remain unchanged. The K-value may in this case be predetermined individually for each consumer in the associated controller system. It is also appropriate, however, to provide the possibility of adjustment during continuous operation. This may be implemented by means of a manually actuateable switch, for example an incremental switch, by means of which the K-value can be varied in specific steps within a range. In another development of the invention, setting takes place automatically as a function of the current pressure level and/or of the currently required flow. This would take, into account the fact that, in the case of a high required hydraulic power, the operator has a different expectation as to the accuracy of the track guidance of the actuators from that in the case of low power.
However, the pump speed may also advantageously be included in the automatic determination of the K-value, since this gives information on the actually available power. If, during operation, there is also information on the current driving state of the vehicle (for example, from the control of the hydrostatic propel drive of a forestry machine or the power-shift transmission of a tractor), then this information is, of course, also of great assistance in determining the optimal K-value. Thus, for example, forestry forwarders load up the logs scattered on the ground partially at a standstill, but partially also during a slow drive movement. In the latter case, of course, a much higher accuracy of track guidance of the crane is required, in order to avoid collisions with the trees which have not been felled and between which the cut-down pieces have to be “fished out”. This must be taken into account via a very high K-value and the resulting minimal mutual influencing.
On many working machines, there are nowadays already mode switches, by means of which the same job can be carried out in different operating modes (“maximum power”, “noise-reduced with reduced engine speed”, etc.). In specific modes, in this case, even individual consumers are switched off entirely. Information on the selected mode and on the actually activatable consumers may, of course, likewise advantageously be included in the setting of the K-value.
Another important parameter is the oil temperature. As is known, the oil viscosity and consequently the friction in the individual components of the hydraulic system are highly temperature-dependent. Friction, in turn, decisively influences the damping of the overall system. By means of a low K-value, low system damping due to temperature can be reacted upon, since a smaller valve opening is a pre-condition for a damping-increasing parameterization of the electronic controllers.
Various alternatives to the elements illustrated in the exemplary embodiment of
Valves may also be equipped directly with two pressure sensors, one each for each working connection. A pressure pick-up “behind the meter-in control edge”, as shown in
The invention forms an improved system for the supply of a plurality of hydraulic consumers, in that the valve of the consumer having the highest load is set, taking into account an additional power loss fraction, at an operating point which corresponds to a wide, but not complete, opening of the valve. The remaining residual opening serves for compensating rapid pressure fluctuations by means of dynamic subcontrollers. The opening of the valve is therefore not adjusted proportionally to the desired flow, as is the case in conventional hydraulic or electronic load-sensing systems.
Dynamic disturbances are compensated only at the consumer valves, not at the pump. At this it is to be assumed that such disturbances are caused primarily by sudden load changes at the consumers. If compensation is not entirely successful at the consumer valves, they also cause oscillations of the pump pressure (secondary disturbance). As a result, even in the case of other consumers, dynamic disturbances occur, although these have themselves not experienced any load change at all. Both types of disturbances are compensated according to the invention solely at the consumer valves. All controller parameterizations are in this case assigned permanently to the respective components. It is not necessary, as is customary, always to change over to a new parameter set for the pump controller when the highest loaded consumer changes. Only the factor K at the valve of the highest loaded consumer serves for setting, while the overall controller structure and parameterization otherwise remain unchanged.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2007 059 491.9 | Dec 2007 | DE | national |
