EP3123033B1 - Verfahren zur bestimmung des hydraulischen arbeitspunktes eines pumpenaggregats - Google Patents

Verfahren zur bestimmung des hydraulischen arbeitspunktes eines pumpenaggregats Download PDF

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Publication number
EP3123033B1
EP3123033B1 EP15719612.2A EP15719612A EP3123033B1 EP 3123033 B1 EP3123033 B1 EP 3123033B1 EP 15719612 A EP15719612 A EP 15719612A EP 3123033 B1 EP3123033 B1 EP 3123033B1
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Prior art keywords
value
variable
ist
pump unit
integral
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German (de)
English (en)
French (fr)
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EP3123033A1 (de
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Tilmann Sanders
Jens Fiedler
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Wilo SE
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Wilo SE
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0088—Testing machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0066—Control, e.g. regulation, of pumps, pumping installations or systems by changing the speed, e.g. of the driving engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps

Definitions

  • the present invention relates to a method for determining a first hydraulic variable of a pump unit operated at a predeterminable speed from a mechanical and / or electrical variable by evaluating a linkage of the hydraulic variable on the one hand and the mechanical or electrical variable on the other hand. Furthermore, the invention relates to a pump control and equipped with a pump control pump unit for performing the method.
  • a method of this kind is known from US 4,108,574 A1 known, in which case the volume flow is determined as the desired size of the delivery, the speed and / or the drive power based on a mathematical linkage of at least one of these variables with the flow rate.
  • EP 2 696 175 A1 describes a method for detecting a flow rate of a centrifugal pump by means of a mathematical model of the pump, which describes the physical relationships of pump and drive motor.
  • the hydraulic operating point in a pump unit is usually defined by the volume flow and the delivery height or the differential pressure applied by the pump. It is displayed in the so-called HQ diagram in which the delivery head or the differential pressure is plotted against the volume flow.
  • HQ diagram in which the delivery head or the differential pressure is plotted against the volume flow.
  • control and regulation methods for pump units that influence these hydraulic variables, in particular regulate along predeterminable characteristics.
  • characteristic curves are customary in which a certain delivery height is kept constant for each volume flow, so-called ⁇ p-c regulations.
  • Another known regulation takes place along characteristic curves which define a linear relationship between delivery height and volume flow, so-called ⁇ p-v regulations.
  • sensors can be used, for example a flow sensor for determination the volume flow or a differential pressure sensor for determining the differential pressure, from which then the head can be calculated.
  • sensors make the production of the pump unit more expensive. It is therefore a concern to renounce them.
  • a hydraulic variable can also be determined mathematically from one or more variables known to the pump unit or its control or regulation, in particular using physical laws of existing physical relationships with the desired hydraulic variable. These relationships can be stored in mathematical form in the control or regulation of the pump unit.
  • the calculation can be made, for example, from the electrical power consumption (motor power or mains input power) resulting from the product of current and voltage. This is a known size of the pump unit, since the current and the voltage is specified depending on the required speed of the pump set by the speed control or regulation, in particular by a frequency converter. In addition, it is particularly easy to measure the current and voltage by electrical means.
  • the performance map can be measured. This means that the power consumption is determined for selected speeds for a large number of volume flows.
  • These values can for example be assigned to one another in a table and stored in the control or regulation of the pump unit.
  • a mathematical function for example a polynomial which describes the relationship between volume flow and power at a specific speed. This function can then be stored alternatively or in addition to the table in the control or regulation.
  • Such a function may for example be formed separately for each speed and used so that the entire performance map is described by a set of functions.
  • a single function can be used that combines the three sizes of power, speed, and flow connected.
  • Using a function instead of a table has the advantage of requiring little storage space because it does not need to store large measurement data. The disadvantage here, however, that the evaluation of the function requires computing power.
  • the use of a function in addition to the table has the advantage that a plausibility check and, if appropriate, an averaging of the value determined from the table and the function can be undertaken.
  • the volume flow can be determined from the table or the corresponding function. From this, in turn, the delivery head can be calculated via the pump characteristic, so that the operating point of the pump unit is obtained.
  • FIG. 1 shows the relationship between the absorbed electric power and the flow rate Q at a pump unit. Shown are four performance curves for different speeds, with the lowest curve being assigned to the lowest speed used and the upper one to the highest speed used.
  • the performance curves make it clear that there is an ambiguity in the characteristic curve in the upper volume flow range, because the characteristic increases steadily up to a maximum with increasing volume flow, but decreases again as the volume flow increases.
  • Q1 12 m 3 / h
  • Q2 16 m 3 / h the same power input of about 250 W before.
  • the problem of the ambiguity of the power characteristic can be circumvented by taking into account only the left part of the power characteristic, ie the volume flow which is smaller than the volume flow present at the maximum of the power characteristic.
  • the hydraulic system of the pump set in this case is designed so that in the intended Operating range, the power is always rising steadily and the maximum flow is where the power has its maximum.
  • a method for determining a first hydraulic variable of a pump unit operated at a predeterminable speed from a mechanical and / or electrical variable by evaluating a linkage of the hydraulic variable on the one hand and the mechanical or electrical variable on the other hand, in which a manipulated variable of the pump unit so with a periodic excitation signal of a certain frequency is applied, that a second hydraulic variable is modulated, wherein from the mechanical or electrical quantity as a system response to the Excitation signal is determined using the linkage of the current value of the first hydraulic variable.
  • This solution resolves ambiguities in the linking of the quantities. It allows a pump set to use the information available to it, i. at least one electrical and / or mechanical quantity, such as the current, the voltage, the electric power, the torque, the rotational speed, or the mechanical power, and without the use of a pressure or flow sensor to close the hydraulic operating point, the For example, by the first and second hydraulic variable, preferably defined by the volume flow and the delivery height.
  • the pump unit may be an electric motor driven centrifugal pump, for example a heating pump in a heating system or a coolant pump in a cooling system.
  • modulating in the sense of the invention is to be understood as a change, but the type, height and speed of the excitation signal are in no way limited. Furthermore, as far as the following is a control of the pump unit, this term is also a regulation to understand, since a scheme includes only a controller with a feedback of a certain size.
  • the current value of the first hydraulic variable can be determined from the amplitude and / or the phase position of the alternating component of the mechanical or electrical variable using the link. This means that initially the alternating component of the mechanical or electrical variable is determined and determines its amplitude or phase position. Subsequently, the combination is used to determine the value of the hydraulic variable from the ascertained amplitude or phase position.
  • the absolute values for the amplitude and phase position are not used here but rather relative values which relate to the excitation signal. In the case of phasing this would mean that it is determined to how much the phase of the system response to the excitation signal is shifted.
  • the link can be given by a table or at least one mathematical function.
  • this table or the at least one function at a certain speed or at a plurality of speeds would associate each value or a number of values of the first hydraulic variable with an amplitude value or phase value of the alternating component.
  • This makes it possible in a particularly simple way to determine the current value of the first hydraulic variable.
  • This assignment is to be carried out by the manufacturer of the pump set by operating the pump set at different speeds by applying the excitation signal and measuring the first hydraulic variable as well as measuring the amplitude and phase angle of the alternating component or calculating it from known relationships. These determined values can then be assigned to one another in tabular form and stored in a control of the pump set.
  • the use of the link can then take place in the case of the table in such a way that the line or column in which a rotational speed corresponding to the current rotational speed is searched for the ascertained amplitude value or phase value. If this or a similar one is found, the value of the first hydraulic variable assigned to the amplitude value or phase value by the corresponding column or row can be determined.
  • a function can be used, resolved to the first hydraulic variable, to calculate the value of the first hydraulic variable from the ascertained amplitude value or phase value. If the link is given by several functions, one of which is valid for a certain speed, first that function must be determined, which is valid for the current speed. In this function then only needs the Amplitude value or phase value to be input. If, on the other hand, the link is given by a single function, then the determined amplitude value or phase value and the current speed must be entered for the function to supply the value of the first hydraulic variable.
  • the product can be formed from the system response and a periodic function of the same or a multiple of the frequency of the excitation signal. Subsequently, the integral of this product over a predetermined, in particular finite integration period is calculated and determined from the value of the integral using the link, the value of the first hydraulic variable. From the value of the integral, the value of the hydraulic variable (Q, H) is then determined using the linkage.
  • the alternating component of the mechanical or electrical variable for example the actual torque, the actual rotational speed or the electrical power consumption of the pump unit.
  • the product would be formed and integrated from the system response and this interchange.
  • the value of the hydraulic quantity (Q, H) is then determined from the value of the integral using the link.
  • the current torque (actual torque), the current speed (actual speed) or the current electrical power consumption can be measured or calculated from other variables. If necessary, measured values must first be preprocessed, for example filtered, before it is suitable for multiplication by the system response. This can be done, for example, by high- or band-pass filtering. With sufficiently large excitation of the system, the alternating component contains a dominant fundamental oscillation which approximately corresponds in phase and frequency to the excitation signal. The result of the integration then corresponds, with the exception of a scaling factor, to the result that would be obtained with a purely mathematical periodic function, for example a sine or cosine function. In particular, the result of this calculation can be linked in the usual way to the first hydraulic variable to be determined, and these can be determined unambiguously.
  • the linking of the hydraulic variable with the mechanical or electrical variable can also be given in the second embodiment in the form of a table or a mathematical function.
  • the first hydraulic variable may each be assigned a value of the integral.
  • This assignment is to be performed by the manufacturer of the pump set at the factory by operating the pump set at different speeds, measuring the first hydraulic variable and calculating the integral as mentioned above or from other known relationships. These determined values can then be assigned to one another in tabular form and stored in a control of the pump set.
  • a value of the integral can be assigned or assigned to each value of the hydraulic variable by the mathematical function at a specific speed. This assignment also assumes that the manufacturer initially measures the pump set by operating the pump set at different speeds, thereby measuring the first hydraulic variable and calculating the integral as previously mentioned or from other relationships known to it. However, these determined integral values are then not stored in a table. Rather, a function, e.g. a polynomial I (Q) is sought which describes a curve on which the measured values of the hydraulic quantity lie.
  • a function e.g. a polynomial I (Q) is sought which describes a curve on which the measured values of the hydraulic quantity lie.
  • a separate mathematical function can be set up for a number of different specific rotational speeds or a general mathematical function (polynomial) can be determined which describes the entire characteristic diagram of the pump set, i. a function (polynomial) I (Q, n) describing the dependence of the integral value on both the first hydraulic quantity (Q) and the speed (n). This also applies to the first embodiment.
  • the periodic function used to multiply the system response is a sine function. It is then possible from the table or the mathematical function directly to determine a value of the first hydraulic quantity, which is assigned to the calculated value of the integral or is assigned by the mathematical function, since the sine function causes the integration leads to a value that plotted against the first hydraulic Size, is unique. This is in FIG. 2 illustrated.
  • the value of the first hydraulic variable associated with the calculated value of the integral can be determined backwards.
  • the second embodiment variant differs from the first embodiment variant only in that the integral values are shown in the table instead of the amplitude values or phase values.
  • the value of the hydraulic quantity can be calculated.
  • the speed is the pump control, for example, known at least in the form of the desired speed.
  • values of the mechanical and / or electrical variable are linked to values of the first hydraulic variable instead of the integral values in the table or the mathematical function, as is known per se in the prior art.
  • the link is given by a table or at least a mathematical function, which is at a given speed any value of the first hydraulic Size assigns a value of mechanical or electrical size.
  • the value of the mechanical or electrical quantity is preferably an average, or in other words, such a value, which is present in the absence of a periodic excitation.
  • the ambiguity can be resolved by using a cosine function as the function with which the system response is multiplied and using the calculated value of the integral to distinguish which part of the table or range of values of the mathematical function to determine the value of the first hydraulic variable valid for the current operating point.
  • a cosine function as the function with which the system response is multiplied
  • the calculated value of the integral to distinguish which part of the table or range of values of the mathematical function to determine the value of the first hydraulic variable valid for the current operating point.
  • the manipulated variable acted upon by the excitation signal is a setpoint speed or a setpoint torque of the pump unit, ie a mechanical size, which is attempted by a regulation of the pump set to keep at a certain value.
  • Speed or torque controls are known per se in pump units.
  • the periodic excitation of the desired speed or the desired torque is a simple measure to achieve a modulation of the second hydraulic variable.
  • the volume flow Q of the pump unit can be used.
  • the second hydraulic variable may then suitably be the delivery head H or the differential pressure ⁇ p .
  • the latter can be easily modulated by modulating the speed or torque of the pump set.
  • the mechanical variable is preferably the torque output by the pump unit or the actual speed of the pump unit.
  • the electrical variable may be, for example, the electric power P el absorbed by the pump unit or the current. The change of at least one of these quantities due to the modulation of the second hydraulic quantity is then considered as a system response.
  • any pairings between the excited manipulated variable and the system response to be analyzed can be used.
  • the target speed can be modulated and the resulting actual speed can be evaluated.
  • the output torque or the electrical power consumption can be used for the evaluation.
  • the target torque can be excited and the resulting actual speed, the torque output or the electrical power consumption are evaluated.
  • the excitation signal is ideally a periodic signal, in particular a sinusoidal signal or a signal containing a sinusoidal function.
  • the latter can also be, for example, a triangular or sawtooth signal.
  • the frequency of the excitation signal is advantageously between 0.01 Hz and 100 Hz.
  • the disadvantage of too low a frequency is the duration of a complete one Period, which is at an excitation frequency of, for example, 0.01Hz at 1 minute and 40 seconds. The longer the period, the greater the likelihood that the hydraulic resistance of the system, and as a result, the operating point of the pump set changes, so that the determination of the current operating point is falsified. Therefore, the excitation frequency should not be too small.
  • the frequency is limited due to the inertia of the rotor, the impeller and the liquid upwards limits.
  • the amplitude of the excitation signal is preferably less than 25% of the speed setpoint. In particular, it can be between 0.1% and 25% of the speed setpoint. At a setpoint speed of, for example, 2000 rpm, a speed fluctuation of ⁇ 2 rpm to ⁇ 500 rpm can thus be suitable.
  • the amplitude of the excitation signal can be calculated from a desired delivery height fluctuation by means of a mathematical equation describing the relationship between the rotational speed and the delivery height at the pump unit.
  • this equation can be derived from the formula describing the stationary relationship between delivery head H, rotational speed n and volume flow Q.
  • H on 2 - BQN - c Q 2 n 2 - bq a n - c Q 2 a - H 0 a - f A .
  • H a 0 n 2 - bq a n - c Q 2 a - on 0 2 - BQN 0 - c Q 2 a - f A .
  • H a 0 n 2 - bq a n - on 0 2 - BQN 0 a - f A .
  • H a 0 n - bq a + bq 2 ⁇ a 2 + n 0 2 - BQN 0 a + f A .
  • H a 0 n - bq a + bq 2 ⁇ a 2 + n 0 2 - BQN 0 a + f A .
  • the integral of the product is calculated from the system response and the periodic function over a period of time T.
  • This integration period T may be one period or may be a multiple of the period of the excitation signal. It is advantageous if the modulation is continuous, ie during the entire operating time of the pump set. In this way, changes in the operating point can be detected immediately. This would not be possible if the method according to the invention would only be used at intervals over a limited period of time.
  • the detection of the mechanical or electrical quantity as a system response to the modulation can be done either at discrete times or continuously.
  • the system response is then presented as a series of values so that multiplication by function and integration of the product thus obtained can occur at any time.
  • At least one further integral can be calculated from the product of the system response and the function over the same integration period, wherein the beginning of this integration period of the further integral is offset in time from the beginning of the integration period of the first integral lies.
  • the calculated values of the integrals can then be combined into an averaged value. This has the effect of smoothing the determined system response.
  • F F (t) 1 (rectangular window)
  • the "cut-out" values are multiplied unchanged with the function and then integrated, ie there is no weighting of the values.
  • Such weighting can be done, for example, by multiplying the system response by a window function that weights the values in the middle of the window more than the values at the edge of the window.
  • a multiplicity of known and in practice usual window functions are available, eg Hamming windows, Gaussian windows, etc.
  • the change in the operating point distorts the value of the calculated integral.
  • this distortion can be at least partially corrected by assuming a linear shift of the operating point and using this in the calculation of the Integrals is corrected.
  • the values of the system response at the beginning and at the end of the integration period are determined, in particular measured, and from these two values a linear change of the system response per time is determined. This linear change is then subtracted from all values of the system response determined in the integration period and only then the integral is formed. In this case, however, the determined values must first be saved.
  • I t 0 + T ⁇ t 0 t 0 + T X t - X t 0 + T - X t 0 T ⁇ t - t 0 ⁇ S t d ⁇ t
  • T k I 2 ⁇ ⁇ ⁇
  • I (t 0 + T ) is the integral to be calculated from time t 0 over the integration period T
  • X (t) is the system response
  • S (t) is the periodic function
  • k l is a positive integer
  • ⁇ is the frequency of the excitation signal f A, n (t), f A, H (t).
  • a pump electronics for controlling and / or regulating the target speed of a pump unit is proposed, which is set up to carry out the method described above.
  • a pump unit comprising such a pump electronics is proposed.
  • the pump unit may be, for example, a heating pump, coolant pump or a drinking water pump.
  • the method according to the invention can be dispensed with volumetric flow sensors. This simplifies structurally the pump housing and reduces the cost of manufacturing the pump set.
  • the pump unit is an electric motor driven centrifugal pump, ideally in wet rotor design. Such can be used in a heating, cooling or drinking water system.
  • the method of hydraulic operating point determination described below also uses information about the dynamic behavior of the system, which is analyzed by a targeted excitation.
  • FIG. 6 A model of the system in which a variant of the method according to the invention can be applied is shown FIG. 6 as a block diagram.
  • a variable-speed centrifugal pump unit 1 is shown, which is connected to a piping system 5 respectively incorporated in this.
  • the system may for example be a heating system, the pump unit 1 corresponding to a heating pump.
  • the piping system 5 is then formed by the leading to the radiators or heating circuits and leading from these to a central heating source lines.
  • water can circulate in the pipelines 5 which is driven by the pump unit 1.
  • the pump unit 1 consists of a pump unit 2, which forms the hydraulic part of the unit 1, an electromotive drive unit 3, which forms the electro-mechanical part of the unit 1, and a control or regulation 4.
  • the drive unit 3 consists of an electromagnetic part 3a and a mechanical part 3b.
  • the control 4 consists on the one hand of software 4a, on the other hand of hardware 4b, which includes the control and / or regulating electronics and power electronics such as a frequency converter.
  • the control electronics 4 is a target speed n 0 specified. From the current current consumption I and the current rotational speed n , the drive unit 3 calculates, for this purpose, a voltage U which is specified for the power electronics 4b, so that the drive unit 3 provides a corresponding electrical power P el .
  • the pump unit 1 thereby generates a delivery height H , which generates a more or less large volume flow Q in the piping system 5 depending on the pipe resistance. From the hydraulic power and thus forming composite losses a hydraulic torque M hyd can be defined, which is counteracted as a braking torque to the motor torque M.
  • the hydraulic variable to be determined is exemplified by the volume flow Q of the pump unit. From the well-known physical-mathematical relationship between volume flow Q and head H at the pump unit 1, the delivery height H can be determined so that the hydraulic operating point [Q, H] of the pump set is fixed.
  • the pump characteristic H P ( Q ) is known by the manufacturer from the measurement of the pump set.
  • the parameters a, b, c are constant characteristics of the pump characteristic.
  • the piping parabola depends on the condition of the piping system connected to the pump unit, whose hydraulic resistance is expressed in the slope d of the piping parabola.
  • the hydraulic resistance is largely determined by the degree of opening of the valves located in the pipeline system, so that the slope d results from the valve position.
  • n should n 0 + f A . n t
  • the amplitude is between 0.1% and 25% of the setpoint speed n 0 and can be factory-set and fixed.
  • H t H 0 + f A .
  • Equation Eq. 8 or 9 can be numerically executed in a microprocessor of the pump electronics 4 or by an analog circuit, as exemplified in FIG. 7 is shown as a block diagram.
  • step S2 follows step S5.
  • the volume flow Q determined as part of the operating point determination in step S5 can then be used directly in equation 8.
  • the excitation frequency f is to be dimensioned such that the delivery height H follows the excitation function f A, H as well as possible despite the inertia of the rotor.
  • a frequency f of 1 Hz is used.
  • the system response following the excitation manifests itself in various physical quantities of the pump set as well as purely mathematically in the models, ie the electric model 4b, electromagnetic model 3a, mechanical model 3b and hydraulic model 2 present quantities. However, it is sufficient to evaluate a single mechanical or electrical size of the pump set.
  • the received electric power P el FIG. FIGS. 1, 2, 3
  • the mechanical torque M mot is used as the system response X (t) to the modulation.
  • the recorded electrical power P el is measured or determined from measured current and measured or calculated voltage.
  • the torque M is can be measured or calculated from the torque-forming current available in the mathematical electromagnetic and mechanical model in the control electronics 4 for performing the control or for monitoring the system.
  • the determination of the power P el and / or the torque M ist can be done by sampling at discrete times or continuously, so that the system response X (t) is present as a discrete or continuous series of measured values or calculated values. This is from step 4 of FIG. 4 includes. For the sake of simplicity, only the case of the continuous series will be dealt with here.
  • the volume flow Q is first determined. This is done by first multiplying the system response X (t) by a periodic function S (t), ie by constructing the product of the system response X (t) and this periodic function S (t).
  • the parameters g 1 , g 2 and k can be selected independently of each other.
  • S sin (t), S cos (t) can in the simplest case have the same periodic basic structure as the excitation signal f A, n (t), f A, H (t), in particular the same frequency ⁇ or f to achieve the result according to the invention.
  • the pump unit as has also been carried out according to the prior art, the manufacturer must be measured on a hydraulic test rig, unless the relationship is known.
  • the relationship between the sought hydraulic variable Q , the rotational speed n and the electrical or mechanical variable P el , M is measured and as a characteristic field as a linkage of the hydraulic variable Q on the one hand with the mechanical or electrical variable M.
  • P el other hand, stored in the form of a table or formula in the pump electronics. 4 Rather, the relationship between actual speed n is , volume flow Q and one of the above-mentioned integrals I (t 0 + T) determined.
  • the integral I (t 0 + T) is calculated by the manufacturer on a hydraulic test stand at a number, in particular a plurality of preset nominal speeds n 0 to a number, in particular a plurality of measured volume flows Q, which is due to the excitation of the system with the excitation signal f A, n (t), f A, H (t) from the product of system response X (t) and the sine or cosine function S sin (t), S cos (t).
  • the simulation curves in FIG. 2 unlike the performance curves in FIG. 1 describe a clear relationship between the volumetric flow and the integral, since the curves increase monotonically over the entire volumetric flow range. This makes it possible, in the intended operation of the pump unit 1 to determine a calculated integral value I (t 0 + T) from the relationship I (Q) determined on the test stand, to determine the currently conveyed volume flow Q. From this, the delivery height H can then be calculated, for example by means of Equation Eq. 1.
  • the value of the first hydraulic variable, the volume flow Q is consequently determined using the relationship.
  • the manufacturer can determine from the values determined on the test stand for each rotational speed n 0 a single mathematical function or a global mathematical function (eg a polynomial) for all rotational speeds, a characteristic curve or, in the case of the global function, a characteristic field describes where all measured values lie.
  • a single mathematical function or a global mathematical function eg a polynomial
  • a characteristic curve or, in the case of the global function, a characteristic field describes where all measured values lie In the case of using several functions, which are valid for each speed, then only the currently valid function must be determined and the calculated integral value used to obtain the corresponding value of the hydraulic variable, ie the volume flow value. If a global function is used to describe the entire characteristic field, the speed and the calculated integral value can be directly used in this equation to obtain the corresponding value of the hydraulic variable.
  • FIG. 3 shows four simulation curves for the integral I (Q) for the same speeds as in FIG. 2 , where also the electric power P el was examined as a system response X (t) , but multiplied by a cosine function S cos (t).
  • the simulation curves in FIG. 3 like the performance curves in FIG. 1 describe no clear relationship between the volume flow Q and the integral I (t 0 + T), since the curves initially fall with increasing volume flow Q, but then rise again.
  • the simulation curves in FIG. 3 reveal a peculiarity, which is that the calculated integral I (t 0 + T). there has the value zero, where the associated power characteristic (see FIG. 1 ) has its maximum.
  • the cosine signal changes the sign exactly at the vertex of the power characteristic, so that the sign of this signal can also serve to identify the operating point, ie right or left of the vertex of the power characteristic.
  • this variant of the method according to the invention is to be used, it is not necessary to determine the volumetric flow and the integral value associated therewith at the manufacturer on the hydraulic test rig at different rotational speeds. Rather, it is sufficient, as in the prior art, to measure the performance map and to determine the threshold value and to deposit it as a table or at least one power characteristic equation in the pump electronics 4. The table or at least one function then assigns a value of the mechanical or electrical variable to the values of the hydraulic variable at a specific speed.
  • At least one further integral I (t 1 + T) may be obtained from the product of the system response X (t) and the function S ( t ) over the same integration period T, wherein the start of integration t 1 of the further integral is offset in time by the offset t 1 -t 0 from the start of integration t 0 of the first integral I ( t 0 + T).
  • the calculated values of the integrals I (t 0 + T) ,, I (t 1 + T) are then averaged to a value.
  • the calculation of the integrals over a finite integration period means that a set of values is cut out of the system response X ( t ), which then represent a "window" of the system response.
  • the correspondingly cut-out windows overlap.
  • FIGS. 8 and 9 show analogous to the FIGS. 2 and 3 a graphic visualization of the linkage of the volume flow Q as a first hydraulic variable with the actual speed as a mechanical variable for four different speeds, wherein in FIG. 8 the amplitude
  • the setpoint speed n is intended by modulating a periodic signal to a static setpoint speed. The actual speed n is then given neglecting disturbances from the sum of the average speed n 0 and the periodic proportion n 1 (t).
  • the phase ⁇ (n 1 ) in FIG. 9 is related to the excitation signal and thus represents a kind of phase shift FIGS. 8 and 9
  • the values shown are measured at the factory and stored as a table or mathematical function in the control of the pump set.
  • and the phase ⁇ (n 1 ) is unique for each speed over the flow rate.
  • the volumetric flow Q which, at the present mean operating rotational speed n 0, of the determined amplitude
  • the method presented here makes it possible in a simple way during operation of the pump set and without the use of a corresponding sensor, a hydraulic variable, e.g. to determine the volume flow.
  • a second hydraulic variable e.g. the delivery height, modulated, in particular to the vibration is excited, which can be done for example by modulation of the target speed or the motor torque as a manipulated variable of the pump unit.
  • the determination of the system response e.g. the actual speed, the output from the pump unit torque or the electric power, and their evaluation by determining the amplitude or phase of the alternating component of the system response or by multiplication with a function of the same frequency as the excitation and integration of the product obtained, obtained are values that mathematically have a clear relationship with the sought hydraulic size. Through the evaluation of this, to be deposited in the pump electronics of the pump unit, the relationship can then determine the value of the sought hydraulic variable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
EP15719612.2A 2014-03-26 2015-03-26 Verfahren zur bestimmung des hydraulischen arbeitspunktes eines pumpenaggregats Active EP3123033B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014004336.3A DE102014004336A1 (de) 2014-03-26 2014-03-26 Verfahren zur Bestimmung des hydraulischen Arbeitspunktes eines Pumpenaggregats
PCT/EP2015/000642 WO2015144310A1 (de) 2014-03-26 2015-03-26 Verfahren zur bestimmung des hydraulischen arbeitspunktes eines pumpenaggregats

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EP3123033B1 true EP3123033B1 (de) 2019-08-21

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EP (1) EP3123033B1 (da)
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EP3816451A1 (de) 2019-10-28 2021-05-05 Wilo Se Verfahren zur bestimmung des volumenstroms einer pumpenanordnung und zugehörige pumpenanordnung
EP4279745A1 (de) * 2022-05-18 2023-11-22 Wilo Se Verfahren zur bestimmung der statischen förderhöhe einer pumpe

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DE102017004097A1 (de) * 2017-04-28 2018-10-31 Wilo Se Verfahren zur Detektion eines abnormalen Betriebszustands eines Pumpenaggregats
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Publication number Publication date
DK3123033T3 (da) 2019-10-28
CN106133327A (zh) 2016-11-16
US20170037857A1 (en) 2017-02-09
DE102014004336A1 (de) 2015-10-01
EP3123033A1 (de) 2017-02-01
CN106133327B (zh) 2018-07-06
US10184476B2 (en) 2019-01-22
WO2015144310A1 (de) 2015-10-01

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