US20160305419A1 - Method for Determining Hydraulic Pressure Parameters in a Displacement Pump - Google Patents

Method for Determining Hydraulic Pressure Parameters in a Displacement Pump Download PDF

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US20160305419A1
US20160305419A1 US14/910,687 US201414910687A US2016305419A1 US 20160305419 A1 US20160305419 A1 US 20160305419A1 US 201414910687 A US201414910687 A US 201414910687A US 2016305419 A1 US2016305419 A1 US 2016305419A1
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Prior art keywords
displacer element
metering chamber
pressure
determined
way
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English (en)
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Steven Liu
Fabian Kennel
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Prominent GmbH
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Prominent GmbH
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Publication of US20160305419A1 publication Critical patent/US20160305419A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/04—Pumps having electric drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/10—Other safety measures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B51/00—Testing machines, pumps, or pumping installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0201—Current
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/04—Motor parameters of linear electric motors
    • F04B2203/0401—Current
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/04—Motor parameters of linear electric motors
    • F04B2203/0402—Voltage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/60—Fluid transfer
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the present invention relates to a method for determining hydraulic parameters in a displacement pump.
  • the displacement pump has a movable displacement element, which bounds the metering chamber, which is connected to a suction and pressure line via valves, with the result that pumped fluid can be alternately sucked into the metering chamber via the suction line and pressed out of the metering chamber via the pressure line by means of an oscillating motion of the displacement element.
  • Displacement pumps additionally have a drive for the oscillating motion of the displacement element.
  • the displacement element is a diaphragm
  • the displacement element is a diaphragm
  • the pressure in the metering chamber will fall, with the result that pumped fluid is sucked into the metering chamber via the suction line.
  • the diaphragm is connected to a thrust member, which is usually mounted pretensioned in a spring-loaded manner at least partially within an electromagnet.
  • the spring-loaded pretensioning ensures that the thrust member and thus the diaphragm remains in a predetermined position, e.g. the second position, i.e. the position at which the metering chamber has the greatest volume.
  • such electromagnetically driven diaphragm pumps are used if the fluid volume to be metered is significantly greater than the metering chamber volume, with the result that the metering rate is essentially determined by the frequency, or the timing, of the current flow through the electromagnet. If, for example, the metering rate is doubled, at the same time a current temporarily flows through the electromagnet twice as frequently, which in turn results in the motion cycle of the diaphragm being shortened and taking place twice as frequently.
  • EP 1 757 809 it is therefore already proposed to provide a position sensor with which the position of the thrust member, or the diaphragm connected thereto, can be determined. By comparing the actual position of the thrust member with a predetermined target position of the thrust member a control of the motion can then take place, with the result that magnetic metering pumps can also be used to convey significantly lower fluid amounts, as the stroke motion no longer takes place abruptly, but rather in a controlled manner.
  • control parameters are determined empirically in each case for different thrust member position states and stored in a memory, with the result that the pump can retrieve and use the corresponding control parameters in dependence on the position of the thrust member.
  • control parameters it is very laborious to determine the control parameters.
  • the control therefore only functions satisfactorily when the system approximately corresponds to the desired state.
  • the control parameters stored in the memory are unsuitable and the control accuracy decreases, with the result that the actual metering profile differs significantly from the desired metering profile.
  • this is undesirable in particular in the case of continuous metering of very small amounts, such as e.g. in the case of the chlorination of drinking water.
  • the control accuracy can, for example, be improved by measuring the density and/or viscosity of the pumped fluid and using the measurement result to select the control parameters.
  • the object of the present invention is therefore to provide a method that allows hydraulic parameters to be determined, such as e.g. the density or the viscosity of the pumped fluid, without additional sensors being required.
  • a physical model having hydraulic parameters is constructed for the hydraulic system, the force exerted by the displacement element on the fluid located in the metering chamber or the pressure in the metering chamber and the position of the displacement element is determined, and at least one hydraulic parameter is calculated by means of an optimization calculation.
  • hydraulic parameters any parameter of the hydraulic system—except the position of the displacement element—which influences the flow of the pumped fluid through the metering chamber.
  • Hydraulic parameters are thus e.g. the density of the pumped fluid in the metering chamber as well as the viscosity of the fluid in the metering chamber. Further hydraulic parameters are, for example, the hose or pipe length and diameter of hoses and pipes which are at least at times connected to the metering chamber.
  • the required determination of the position of the displacement element can take place via the position sensor which is usually present in any case.
  • the speed and acceleration of the displacement element can be determined from the position of the displacement element.
  • the current through the electromagnetic drive can be measured and the force exerted by the displacement element on the fluid located in the metering chamber is determined from the measured current and the measured position of the displacement element.
  • a separate pressure sensor is not necessary.
  • the present method can, of course, also be used with a separate pressure sensor.
  • valve to the suction line is open and the valve to the pressure line is closed.
  • a flexible hose which ends in a storage tank at ambient pressure is usually mounted on the valve to the suction line.
  • Optimal parameters are the parameters which best describe the system, i.e. for which the difference between the model and the measured situation is at a minimum.
  • the determination method according to the invention could essentially take place simply through a repeated analysis of the suction stroke behavior.
  • the physical model of the hydraulic system can also be considered for the case that the valve to the suction line is closed and the valve to the pressure line is open.
  • the pump manufacturer as a rule does not know at first in what environment the metering pump is used, and therefore also does not know the pipe system attached to the pressure valve which connects the pressure line to the metering chamber, only a generalized assumption can be made here. Without knowledge of the pipeline system attached to the pressure valve, the constructed physical model can therefore not be constructed as accurately as is the case in the described simplest form for the hydraulic system during the suction stroke.
  • valve opening time points are measured or determined and the respectively appropriate physical model is selected in dependence on the result of the determination of the valve opening time points.
  • the method according to the invention is then carried out separately for the suction stroke and the pressure stroke.
  • values are obtained for the hydraulic parameters, such as e.g. the density and the viscosity of the pumped fluid, which do not correspond exactly in practice. In principle it would therefore be possible to take the average of the different values, wherein it must possibly be taken into account that because of the better description of the actual situation by the physical model during the suction stroke, the value obtained during the suction stroke is weighted more heavily in the averaging than the value ascertained during the pressure stroke.
  • the constructed physical model can be used with the hydraulic parameters determined in this way in order to determine, for its part, the pressure in the metering chamber.
  • a model-based control in particular a nonlinear model-based control is used for the drive of the displacement element.
  • a suitable manipulated variable can then also be calculated.
  • a characterizing feature of such a model-based control is thus the constant calculation of the necessary manipulated variables on the basis of measured variables using the system variables given by the model.
  • the underlying physical system is described approximately mathematically by the modeling. This mathematical description is then used to calculate the manipulated variable on the basis of the obtained measured variables. Unlike the known metering profile optimization methods, the drive is thus no longer seen as a “black box”. Instead, the known physical relationships are used to determine the manipulated variable.
  • the position of the displacement element and the current through the electromagnetic drive are measured and a state-space model is used for the model-based control, which uses the position of the displacement element and the current through the magnetic coil of the electromagnetic drive as measured variables.
  • the state-space model does not have any further measured variables to be detected, i.e. the model is developed such that it makes a prediction for the immediately following motion of the thrust member solely on the basis of the detected thrust member position and the detected current through the magnetic coil.
  • the determined hydraulic parameters are used.
  • a state-space model is usually meant the physical description of a present system state.
  • the state variables can describe the energy content of the energy storage elements contained in the system.
  • a differential equation of the displacement element can be used as model for the model-based control.
  • the differential equation can be an equation of motion.
  • an equation of motion is meant a mathematical equation which describes the spatial and temporal motion of the displacement element under the effect of external influences.
  • displacement pump-specific forces which act on the thrust member are modeled in the equation of motion.
  • the force exerted on the thrust member by a spring, or the spring constant k thereof, and/or the magnetic force exerted on the thrust member by the magnetic drive can be modeled.
  • the force exerted on the thrust member by the pumped fluid can then be treated as a disturbance variable.
  • this disturbance variable can then likewise be modeled using the determined hydraulic parameters.
  • the system is influenced in a corrective manner.
  • the influence of the available manipulated variables on the controlled variable can be simulated.
  • the control strategy which is best at that time can then be selected adaptively.
  • a nonlinear state-space model is therefore chosen as state-space model and the nonlinear control takes place either via control-Lyapunov functions, via flatness-based control methods with flatness-based feedforward control, via integrator backstepping methods, via sliding mode methods or via predictive control.
  • Nonlinear control via control-Lyapunov functions is preferred.
  • Control-Lyapunov functions are, for example, a generalized description of Lyapunov functions. Appropriately chosen control-Lyapunov functions lead to a stable behavior in the framework of the model.
  • the model which forms the basis of the model-based control is used to formulate an optimization problem, in which, as a secondary condition for optimization, the electric voltage in the electric motor and thus the energy fed to the metering pump is as small as possible, but at the same time it is achieved that the actual profile approaches the target profile as quickly as possible and with as little overshooting as possible.
  • the measured signals are filtered using a low-pass filter before the processing in the underlying model in order to reduce the influence of noise.
  • a self-learning system is realized here.
  • the model-based control according to the invention has already led to a significant improvement in the control behavior, there can still be deviations between the target profile and the actual profile. In particular, this cannot be avoided in the case of energy-minimizing selection of the control intervention.
  • the deviation during a cycle is detected and in the next cycle the detected deviation is at least partially subtracted from the desired target position profile.
  • a subsequent pressure-suction cycle is deliberately provided with a “false” target value profile, wherein the “false” target value profile is calculated from the knowledge obtained in the preceding cycle. Namely, if in the subsequent suction-pressure cycle there is exactly the same deviation between actual and target profile as in the previous cycle, the use of the “false” target value profile leads to the actual desired target value profile being achieved as a result.
  • the difference between actual and target profile is determined at regular intervals, best of all in every cycle, and is taken into account correspondingly in the subsequent cycle.
  • the difference between actual and target profile is measured over several cycles, e.g. 2, and from this an average difference is calculated, which is then at least partially subtracted from the target profile of the subsequent cycles.
  • any of the functions dependent on the detected difference can be used for correcting the next target position profile.
  • the modeling according to the invention can be used in order to determine a physical variable in the displacement pump.
  • the fluid pressure in the metering chamber can be determined.
  • the equation of motion of the displacement element takes into account all forces which act on the displacement element. In addition to the force applied to the displacement element by the drive, this is also the counterforce applied to the diaphragm and thus to the displacement element by the fluid pressure in the metering chamber.
  • a warning signal can be emitted and the warning signal can be sent to an automatic shutoff, which shuts off the metering pump in response to the warning signal being received. Therefore, if for any reason a valve does not open or the pressure on the pressure line increases sharply, this can be ascertained by the method according to the invention without using a pressure sensor and the pump can be shut off as a precaution.
  • the displacement element, with the associated drive additionally takes over the function of the pressure sensor.
  • a target fluid pressure curve, a target position curve of the displacement element and/or the target current progression through the electromagnetic drive is stored for a motion cycle of the displacement element.
  • the actual fluid pressure can be compared with the target fluid pressure, the actual position of the displacement element with the target position of the displacement element and/or the actual current through the electromagnetic drive with a target current through the electromagnetic drive and, if the differences between actual and target value satisfy a predetermined criterion, a warning signal can be emitted.
  • the warning signal can, for example, activate an optical indicator or an audible alarm.
  • the warning signal can, however, also be directly made available to a control unit, which takes the appropriate measures in response to the warning signal being received.
  • the difference of the actual and target value is determined for one or more of the measured, or determined, variables, and if one of the differences exceeds a predetermined value a warning signal is emitted.
  • a weighted sum of the relative deviations from the target value can be determined and the criterion can be chosen such that a warning signal is emitted if the weighted sum exceeds a predetermined value.
  • Different weighting coefficients can be assigned to the different error events. In the ideal case, precisely one criterion is satisfied when an error event occurs, with the result that the error event can be diagnosed.
  • the temporal gradient of a measured or determined variable is therefore ascertained and, if this exceeds a predetermined threshold value, the valve opening or valve closing is diagnosed.
  • the mass m of the displacement element, the spring constant k of the spring which pretensions the displacement element, the damping d and/or the electrical resistance R Cu of the electromagnetic drive is determined as physical variable.
  • all of the named variables are actually determined. This can take place, for example, by a minimization calculation. All of the named variables, with the exception of the pressure in the metering chamber, represent constants which can be determined by experiment and which as a rule do not change during the operation of the pump. Nevertheless, symptoms of fatigue of the different elements can occur which change the value of the constants. For example, the measured pressure-path progression can be compared with an expected pressure-path progression. The difference of both gradients integrated over a cycle can be minimized by varying the constant variables. If e.g. it is established that the spring constant has changed, a defective spring can be diagnosed.
  • Such a minimization could also be carried out in the unpressurized state, i.e. when there is no fluid in the metering chamber.
  • FIG. 1 a schematic representation of the suction line attached to the displacement pump
  • FIGS. 2 a -2 e example of hydraulic parameters and the time-dependent development thereof
  • FIG. 3 a schematic representation of an ideal motion profile
  • FIG. 4 a schematic representation of the self-learning function
  • FIG. 5 a schematic representation of a pressure-path diagram and a path-time diagram for the normal state
  • FIG. 6 a schematic representation of a pressure-path diagram and a path-time diagram for a state with gas bubbles in the metering chamber.
  • the position of the displacement element, or the speed and acceleration of the displacement element determined therefrom, and the pressure in the metering chamber which can be determined via the force exerted on the pumped fluid by the diaphragm serve as measured variables, or external variables to be determined.
  • the suction line consists of a hose which connects the suction valve to a storage tank, for the suction stroke, i.e. while the pressure valve is closed and the suction valve is open, the hydraulic system can be described in a simplified manner, as is represented in FIG. 1 .
  • the suction line consists of a hose with the diameter D S and the hose length L.
  • the hose bridges a height difference Z.
  • the nonlinear Navier-Stokes equations can be simplified if it is assumed that the suction line has a constant diameter and is not expandable and that an incompressible fluid is used.
  • the hydraulic parameters are now determined which can best describe the measured position of the thrust member and the measured or determined pressure in the metering chamber using the constructed model as a basis.
  • the parameters determined by the method according to the invention can then, in turn, be used together with the constructed physical model to determine the force exerted on the thrust member by the hydraulic system.
  • This information can be used for the control.
  • the model developed here can physically model the effect of the hydraulic system and take this into account in the form of a disturbance variable feedforward.
  • a magnetic metering pump has a movable thrust member with a connecting rod firmly connected thereto.
  • the thrust member is mounted to be axially movable in the longitudinal axis in a magnetic casing which is firmly anchored into the pump housing, with the result that when the magnetic coil in the magnetic casing is electrically triggered, the thrust member with connecting rod is drawn into a hole of the magnetic casing against the action of a pressure spring, and after the magnet is deactivated the thrust member travels back into the starting position by means of the pressure spring.
  • the pressure stroke and the suction stroke do not necessarily have to last for the same amount of time.
  • the metering chamber is merely filled again with pumped fluid, it is advantageous to carry out the suction stroke as quickly as possible in each case, wherein care is nevertheless to be taken there is no cavitation in the pressure chamber.
  • the pressure stroke can last a very long time, in particular in application cases in which only very small fluid amounts are to be metered. This results in the thrust member moving only gradually in the direction of the metering chamber.
  • the motion of the thrust member In order to achieve a motion of the thrust member as is represented in an idealized manner in FIG. 3 , the motion of the thrust member must be controlled. Only the position of the thrust member and the size of the current through the magnetic coil are customarily available as measured variables.
  • a (nonlinear) model is therefore developed, which describes the state of the magnetic system.
  • N 1 number of turns
  • the model can be used in order to calculate the likely effect of a control intervention.
  • this difference is measured during a pressure-suction cycle and the sum of the measured difference and the desired target profile is used as target profile for the subsequent cycle.
  • the fact that the pressure-stroke cycle repeats is utilized.
  • a target value profile which differs from the actual desired target value profile is thus specified.
  • This self-controlling principle is represented schematically in FIG. 4 for the purpose of clarification.
  • the position of the thrust member is represented on the y-axis and the time is represented on the x-axis.
  • a target profile used for the control is represented with a dashed line.
  • This target profile corresponds to the desired target profile which is modeled as a reference profile for comparison in the third cycle.
  • the actual profile will deviate from the target profile.
  • an actual profile is therefore represented by way of example with a continuous line.
  • the deviations between actual and target profile are represented in a more pronounced manner than they occur in practice.
  • the difference between the actual profile of the first cycle and the reference profile is then subtracted from the target profile used for the first cycle and the difference is used as target profile for the control during the second cycle.
  • the thus-obtained target profile is represented dashed in the second cycle.
  • the actual profile deviates from the target profile used to the same extent as was observed in the first cycle. This results in an actual profile (drawn in with a continuous line in the second cycle) which corresponds to the reference profile.
  • F P i.e. the force on the thrust member through the fluid pressure in the conveying chamber
  • the state variables of the system models are evaluated and the pressure in the pump head of the electromagnetic metering pump is determined.
  • the necessary current and position sensors are already built in the pump system for the purposes of control technology, with the result that the information is already available without the construction of the metering pump needing to be supplemented.
  • the diagnosis algorithms can then be performed.
  • the model-based diagnosis of excess pressure in the process and the automated pump switch-off can be realized.
  • the valve opening and valve closing time points can, for example, be identified via the determination and evaluation of temporal gradients of coupled state variables of the system model. It can be detected when the state gradients overshoot or fall short by means of predetermined limits, which leads to the identification of the valve opening and valve closing time points.
  • the pressure can also be determined in dependence on the position of the thrust member and the valve opening and valve closing time points can be derived from an evaluation.
  • a corresponding pressure-path diagram is represented on the left in FIG. 5 .
  • the associated path-time diagram is represented on the right in FIG. 5 .
  • the corresponding pressure-path diagram is shown on the left in FIG. 5 . It will proceed in the clockwise direction, starting at the coordinate origin at which the thrust member is located in the position 1 .
  • the pressure in the metering chamber will first increase sharply until the pressure is able to open the valve to the pressure line. Once the pressure valve is open, the pressure in the metering chamber remains essentially constant.
  • the opening point is indicated with the reference number 2 . From this time point, which is also recorded on the right in FIG. 5 , a metering takes place. With each further motion of the thrust member, metering fluid is pumped into the pressure line.
  • the valve closing time points can be determined from the path-time diagram, as they lie at the displacement maxima of the thrust member.
  • the time points 2 and 4 i.e. the valve opening time points are not as easy to determine, especially as in practice the pressure-path diagram has rounded “corners”. Starting from position 1 in the pressure-path diagram, for example, when 90% of the pressure maximum is reached (known from position 3 ), the path can therefore be read off and the increase of the pressure-path diagram between points 1 and 2 can be determined.
  • the 90% curve is drawn in dotted.
  • the time point 4 can also be determined in the same manner. This determination can take place in each cycle and the result used for a later cycle. Changes in the opening time points can thereby also be detected.
  • gas bubbles in the hydraulics system can be diagnosed.
  • cavitation in the pump head of the metering unit and/or valve opening and valve closing time points of the metering units can be diagnosed.
  • this can trigger a warning signal and corresponding measures.
  • FIG. 6 An example is shown in FIG. 6 .
  • the pressure-path diagram is represented on the left and the path-time diagram is represented on the right.
  • the right-hand figure is identical to the corresponding diagram of FIG. 5 .
  • a clear shift in the valve opening time points can thus be used to diagnose the state “air in the metering chamber”.
  • cavitation only the valve opening time point 4 ′ shifts and not the valve opening time point 2 , with the result that such a behavior can be used to diagnose the state “cavitation”.
  • model-based methodology presented enables an essentially more comprehensive and more valuable diagnosis than has been realized to date.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)
US14/910,687 2013-08-29 2014-08-21 Method for Determining Hydraulic Pressure Parameters in a Displacement Pump Abandoned US20160305419A1 (en)

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US20160201657A1 (en) * 2013-08-29 2016-07-14 Prominent Gmbh Method for Improving Metering Profiles of Displacement Pumps
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EP4311937A1 (fr) * 2022-07-28 2024-01-31 Prognost Systems GmbH Procédé de surveillance automatique d'une machine à piston, machine à piston pouvant être surveillée par le procédé et programme informatique avec mise en oeuvre du procédé

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HK1220751A1 (zh) 2017-05-12
ES2648915T3 (es) 2018-01-08
EP3039289A1 (fr) 2016-07-06
DE102013109411A1 (de) 2015-03-05
WO2015028386A1 (fr) 2015-03-05
DK3039289T3 (da) 2017-11-27
JP2016529441A (ja) 2016-09-23
CN105492767A (zh) 2016-04-13
CA2920224A1 (fr) 2015-03-05
KR20160046855A (ko) 2016-04-29
EP3039289B1 (fr) 2017-09-27
CA2920224C (fr) 2021-03-09

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