EP2469094B1 - Procédé de fonctionnement d'un agrégat de pompes doubles ou multipompes - Google Patents

Procédé de fonctionnement d'un agrégat de pompes doubles ou multipompes Download PDF

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Publication number
EP2469094B1
EP2469094B1 EP11009716.9A EP11009716A EP2469094B1 EP 2469094 B1 EP2469094 B1 EP 2469094B1 EP 11009716 A EP11009716 A EP 11009716A EP 2469094 B1 EP2469094 B1 EP 2469094B1
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EP
European Patent Office
Prior art keywords
pump
load
value
speed
rotational speed
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EP11009716.9A
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German (de)
English (en)
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EP2469094A3 (fr
EP2469094A2 (fr
Inventor
Jürgen Hübner
Christian Roos
Sergej Merkel
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Wilo SE
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Wilo SE
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Publication of EP2469094A3 publication Critical patent/EP2469094A3/fr
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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
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/029—Stopping of pumps, or operating valves, on occurrence of unwanted conditions for pumps operating in parallel

Definitions

  • the present invention relates to a method for operating a pump unit with at least one base load-operated first pump and at least one second peak-load pump, which is switched on as needed and operated in parallel to the at least one first pump, wherein the pump unit regulated in such a predetermined control characteristic will be that the recorded power is minimal. Furthermore, the invention relates to a computer program with instructions for carrying out this method and a pump unit of the type mentioned with an electronic control system, which is set up for carrying out the method according to the invention.
  • Pump units consisting of two parallel pumps are called double pumps.
  • pumps with more than two parallel pumping pumps are called multipumps or pressure stations.
  • the pumps are usually driven by an electric motor.
  • the fields of application of such pumps are, for example, in heating systems as circulating pumps or in the supply of fresh water for pressure generation.
  • a double pump and a corresponding control thereof is for example from the European patent specification EP 0 864 755 B1 known. Further shows also the EP 2 161 455 A1 a double pump.
  • Two different control concepts can be used for the control of double or multi-pumps.
  • the pumps of the unit over the entire control range to cover the required flow rate synchronously, ie operated at the same speed.
  • initially only one of the pumps of the pump unit is used to cover a required delivery flow.
  • This pump is called base load pump and is responsible for covering the flow rate in the so-called base load range.
  • the second or a second pump is connected, then to deliver the required flow together with the base load pump.
  • This second or further pump can be referred to as peak load pump, which allows with its additional hydraulic power that the double pump or multi-pump unit operating points beyond the maximum characteristic of the base load pump, ie achieved in the so-called peak load range.
  • peak load pump two or more pumps can be jointly responsible for covering the base load and therefore together form a base load pump to which a peak load pump isstructureschaltbar. Subsequently, therefore, "base load pump” is used in the singular, knowing that for the purposes of this application, two or more pumps can be understood by it.
  • the base-load pump is operated at maximum speed, whereas the peak-load pump delivers only that hydraulic power contribution that is required to achieve the additionally required delivery flow. If the operating point can not be reached in a multi-pump unit with the second or further, connected pump at maximum speed, then another pump is connected. This is done until the required flow rate is reached.
  • the peak load range in a double pump and multi-pump unit includes all those operating points in the characteristic field that are not reachable by the base-load pump alone.
  • the base load range includes all those operating points that can basically be achieved by the base-load pump alone.
  • a performance-optimized operation in double pumps and multipumps is therefore achieved in that in the said characteristic range a peak load pump is connected and both or all pumps run synchronously. Such operation at a reduced speed is then energetically cheaper than a sole operation of the base load pump with a correspondingly high speed.
  • a boundary line which characterizes the theoretical transition between the operation of the pump unit in the base load range with only the base load pump to the efficiency-optimized range with base load and peak load pump is according to the prior art in the control electronics of the pump unit deposited.
  • operation of the pump unit can then be determined by measuring the differential pressure between the suction side and pressure side and estimating or measuring the flow, if an operating point of the unit is below the limit and thus only the base load pump should be operated, or if the operating point is above the limit line and The pump set should be operated with base load and peak load pump.
  • the limit line therefore indicates for each delivery pressure at which volume flow the peak load pump should be connected for energy reasons.
  • the object of the present invention is to operate a double pump or multi-pump aggregate efficiency-optimized, without a prior metrological recording and evaluation of characteristics of the pump set is required to determine the limit for switching from base load operation in the peak load operation.
  • a method for operating a pump unit having at least one base load-operated first pump and at least one second-pump operating at peak load, which is activated as needed and operated in parallel to the at least one first pump, with the pump unit being regulated on a predetermined control characteristic in that the power consumed is minimal, wherein the pump unit is operated in dependence on an upper and a lower limit either with at least two pumps or with at least one pump switched off, starting from a synchronous operation of the pumps at an operating point in which the pumps with operated in the same speed and / or power, in a first step, the value of at least one operating variable of the pump unit is stored as a reference value, in a second step, the funded by the second pump flow is reduced in one third step depending on the reactions of the regulated first pump a Assignment of the operating point to a load range is done and replaced in a fourth step, the upper or lower limit by the reference value.
  • the inventive method makes it possible to make do without the measurement of the characteristic area of the pump unit before its commissioning. Rather, the boundary line or the switching point for a set during operation of the pump set control characteristic during operation is determined as a kind of "limit band". This is done by determining at each current operating point whether this operating point lies in the peak load range, in the efficiency-optimized range or in the base load range of the pump set, the limit band being limited in its width by the lower and upper limit values. A measurement of the volume flow, the delivery head or the differential pressure for the determination of the switching point is no longer necessary by the proposed method.
  • a particular advantage of the method according to the invention is that the position and width of the boundary strip are adapted and reduced during operation of the pump unit. This causes wear and wear on the pump set to require no change in the operating setting. Also, software and / or firmware updates remain unaffected.
  • the pump set is always operated energy-optimized.
  • the synchronous speed of the pump unit is used as the operating variable for determining the upper and lower limit values, and these are stored as a reference speed.
  • the synchronous speed is that speed at which the base-load pump and the peak load pump are operated synchronously, ie at the same speed.
  • the rotational speed can be determined in a simple manner, for example by calculation on the basis of current and voltage, which are determined metrologically or present numerically in a model (observer). Alternatively, the speed may be determined by means of a speed sensor well known in the art.
  • the electrical power consumed by the pump unit can also be used as the operating variable.
  • the volume flow delivered by the second pump can be reduced by reducing the speed of the second pump. This can be done in a simple manner by appropriate control of the pump. Alternatively, the volume flow of the second pump can also be reduced in that an arranged between the second pump and the confluence point of the flow rate of the second pump to the total volume flow of the pump unit valve is increasingly closed. However, this requires additional structural and control measures on the pump unit.
  • the power absorbed by the pump unit in synchronous operation can be determined and stored as a reference power. This makes it possible to carry out a performance comparison of the absorbed power of the pump unit for the assignment of the current operating point to a load range, in particular to the efficiency-optimized range. The comparison of the power is then carried out before the reduction of the volume flow of the second pump and after the reduction of this volume flow.
  • the reference value in particular the reference speed as an upper limit, in particular a speed limit can be stored if after the volume flow reduction at least a first condition is met, which is assigned to one of the load areas peak load range or efficiency-optimized range.
  • a first condition is met, which is assigned to one of the load areas peak load range or efficiency-optimized range.
  • the reference value in particular the reference speed can be stored as a lower limit, in particular speed limit, when at least one second condition is assigned, which is assigned to the base load range. If this second condition is satisfied, it can thus be determined that the current operating point of the pump set lies in the base load range.
  • the reference value is set as the lower limit value.
  • the reference value is set as the upper limit value.
  • This procedure can be performed according to the invention for all operating points on a respectively set control characteristic of the pump unit on which the pump unit is operated according to a higher-level control, the upper and lower limit is dynamically adjusted during operation, if a new operating point is present closer to the theoretical limit line.
  • the pump unit according to the invention is provided with at least two pumps, i. in the case of a double pump operated with both pumps. Further, the pump set will be at the lower limit or below the lower limit with at least one pump off, i. operated in the case of a double pump with only one pump. If the synchronous rotational speed of the pump assembly used by the process according to the invention always starts when a new operating point sets, it can be easily determined on the basis of a comparison of the current synchronous rotational speed with the stored upper rotational speed limit value and the stored lower rotational speed limit value whether the current operating point is equal to or above the upper limit value or equal to or below the lower limit value. In these cases no adjustment of the limit values takes place.
  • the method according to the invention is carried out separately for each predetermined control characteristic.
  • an upper and a lower limit of the operating variable, in particular the synchronous speed is set on each control characteristic on which a higher pressure regulator regulates the pump unit, between which the transition from the base load range to the efficiency-optimized range and depending on which the unit with at least one shut down pump or at least two pumps is operated.
  • the control characteristic may be such a characteristic in which the pressure generated by the pump unit is kept constant over the volume flow. Such a control characteristic is known as ⁇ p-constant characteristic. Alternatively, control characteristics are known in which the pressure of the pump unit is adjusted proportionally to the volume flow. Such characteristics are known as ⁇ p-variable. Since the transition from the base load range to the efficiency-optimized range for each control characteristic lies at a different operating point, it makes sense, when the current control characteristic changes, to determine the determined limit values in a characteristic-specific manner, ie. store assigned to this last characteristic. Thus, in the case that is changed back to a previous control characteristic, the limit values previously determined for this control characteristic can be reused.
  • new limit values are used when changing the control characteristic. Like the limit values for the previous control characteristic, these new limits are set to initial values and then determined numerically based on the setting of operating points. In this case, the synchronous speed can be used again as a reference variable.
  • the reference value of the operating variable can be stored as an upper limit value if, after the volume flow reduction, in particular the speed reduction of the second pump, at least one first condition is met.
  • This condition may be, for example, reaching or exceeding the maximum speed of the first pump. If this condition is met, it follows from the conclusion that the current operating point is in the peak load range, in which a flow is required, which can not be supplied by the at least one base load pump alone. Because by reducing the volume flow, in particular the speed of the second pump, the base load pump must apply the missing flow rate of the second pump, i. be operated at a higher flow rate. If the speed of the base-load pump rises to or above the maximum speed with this volume flow transfer, the first condition would be met and the current operating point is in the peak load range.
  • a comparison with the stored reference power may be used as the first condition, wherein the current power consumption of the first pump, i. the base-load pump is compared with this reference power and is checked as the first condition exceeding this reference power. With this condition, it can be determined whether the current operating point of the pump set is in the efficiency-optimized range.
  • This finding is based on the finding that, in the case of a current operating point of the pump set, the first pump can achieve an assumption of the volume flow of the second pump below the maximum speed characteristic of the first pump.
  • the power consumption of the base-load pump is higher than the previously recorded in synchronous operation of the pump unit with base load pump and peak load pump power, it is energetically favorable to operate for this operating point, the base load pump and the peak load pump simultaneously, in particular synchronously.
  • Increases The power consumption of the first pump after the volume flow reduction of the second pump via the stored reference power it is thus determined that the current operating point is in the effective wheel-optimized range of the characteristic field of the pump unit.
  • the comparison of the power consumption to the stored reference power represents the stricter criterion, because even in the case of an operating point in the peak load range, the power of the base-load pump will rise above the reference value.
  • the two aforementioned first conditions can also be applied in a commuative manner, whereby they are examined in a ranking order.
  • the exceeding of the maximum speed of the first pump can be checked and, if this maximum speed is not reached or exceeded, the current power consumption of the first pump determined and compared with the stored reference power.
  • the speed can be easily determined because the higher-level pressure regulator, which regulates the pump set to a predetermined control characteristic, outputs a speed setpoint, the amount of which can be easily determined. If this reaches a maximum value, the resource-intensive and more complex metrological and mathematical determination of the power consumption of the first pump or a numerical comparison of this value with the stored reference power can be saved.
  • the reference value of the operation quantity may be stored as a lower limit value when at least a second condition associated with the base load range is satisfied.
  • a second condition the case may be used that the power consumption of the first pump in response to a volume flow reduction of the second pump, at least on average substantially no longer changed, ie in particular no longer increased. This condition is reached at an unchanged operating point in the base load range at some point.
  • the volume flow reduction should be carried out continuously or successively stepwise such that the time period from the last to the next reduction is less than the time constant of the system response to the volume flow reduction. The following is true Consider: starting from a synchronous operation of the first and the second pump, these contribute 50% to the volume flow of the pump set.
  • this criterion can be used as a second condition of the case that the volume flow or the speed of the second pump due to the reduction reaches or falls below a minimum value.
  • This criterion can be used if the former criterion is not met, i. the power consumption of the first pump, in particular fluctuates on average, so that on the basis of this determination can not be made a clear statement about the operating point, unless in any case the power consumption does not rise above the stored reference power.
  • the volumetric flow of the second pump in particular the rotational speed of the second pump, is gradually reduced to such an extent that the volumetric flow and / or the rotational speed reaches or falls below a minimum value and the power consumption of the first pump is still not exceeded the stored reference power has risen, this is a proof that the current operating point of the pump unit is in the base load range, the required flow can be provided by the base load pump alone and the operation of the base load pump alone causes a lower power consumption of the pump unit, as if base load - And peak load pump are operated synchronously.
  • the value of an operating variable of the first pump is additionally stored as the base load reference value.
  • This base load reference value represents a comparison value with which the current value of the considered operating variable of the first pump in the base load operation can be compared in order to detect a change in state of the first pump.
  • the base load operation here is that operation in which only the at least one base load pump operates, i. in which at least one pump of the pump set is switched off.
  • its speed can be used as the operating variable of the first pump, since it can be determined in a simple manner on the basis of the speed information of the superordinate pressure regulator of the pump unit.
  • the volume flow reduction of the second pump can take place stepwise or continuously. This has the advantage over an abrupt shutdown of the second pump that the higher-level pressure regulator is not affected in its control task and a sudden pressure drop in the hydraulic system is avoided. In addition, responding to a sudden volume flow request quickly by re-starting the second pump.
  • a stepwise reduction can be made with values between 200 rpm and 50 rpm, in particular about 75 rpm to 150 rpm, preferably about 100 rpm.
  • this can be done, for example, with a negative slope of 50-150 U / min per second, in particular 100 U / min per second.
  • the volumetric flow reduction it is possible after the volumetric flow reduction to return to the synchronous operation of the pump unit when the power consumption of the first pump decreases.
  • This can be used as a third condition that is applicable in addition to the other two conditions. It is fulfilled when, during the implementation of the method steps according to the invention, in particular after the volume flow reduction, the required delivery rate decreases, i. the operating point of the pump set changes in the direction of low volume flows. In this case, checking the first and second conditions would be negative. For this reason, it is advantageous, in the case of a sinking power consumption of the first pump after the volume flow reduction of the second pump to return to the synchronous operation and continue from this operation, the method, i. repeat the assignment of the new operating point to one of the load ranges.
  • the third condition is thus a fallback condition.
  • volume flow of the second pump is further reduced if none of the conditions is met. In any case, this can be done as long as no minimum value for the volume flow, in particular the minimum speed of the second pump, has yet been reached.
  • each state of the method according to the invention can be converted into a synchronous operation, when the first pump reaches an inadmissible operating state, in particular when the speed of the first pump reaches or exceeds a maximum value.
  • This procedure takes into account the fact that in the short term, an increased volume flow demand can be made of the pump unit, which can not be operated with the operation of one or more base-load pump alone. Accordingly, in this case, all pumps of the pump set are switched on again and operated synchronously, so that the method for the changed operating point can start anew.
  • the first condition is immediately returned to the synchronous mode and the reference value is stored as the upper limit value only when the operating state before the volume flow reduction is restored after the return.
  • This procedure represents a plausibility check and takes into account the case that changes during the review of the first condition of the operating point of the pump set. Because only in the case of no change in the operating point, the pump unit will return to the original operating state in the reversal of the volume flow reduction, in which the synchronous speed and / or power consumption of the pump unit again corresponds to / before the volume flow reduction. Only in this case is it possible to conclude that the operating state is in the peak load range or in the efficiency-optimized range, so that the reference value can be correctly stored as the upper limit value.
  • the lower limit is reset to a minimum value and is returned to the synchronous operation, when the first pump reaches an inadmissible operating state in the base load operation, in particular reaches or exceeds a maximum speed.
  • the above-described method can be implemented in a computer program, i. be formed by a computer program product containing instructions for carrying out the method according to the invention, and which is carried out when it is executed on a microcomputer of a control electronics.
  • the method can be implemented both in a control electronics of the pump unit and in an external control device, in particular in a control computer.
  • the invention relates to a pump unit with at least one base load-operated first pump and at least one second peak-load pump, which is switched on and operated parallel to the at least one first pump, wherein the pump unit is controllable on a predetermined control characteristic that the recorded power is minimal, and wherein it has a control electronics, which is adapted to carry out the method described above.
  • the aforementioned computer program with the instructions for carrying out the method can be loaded onto a microcomputer of the control electronics.
  • FIG. 1 shows a schematic representation of a double pump, ie a pump unit 1 with two identical pumps 2a, 2b, which are hydraulically connected in parallel. They have a common suction line 4, to which the two pumps 2a, 2b are connected with their suction side. On the pressure side, the pumps 2 a, 2 b open into a common pressure line 5, wherein a check valve 3 a is arranged in the transition region to the pressure line 5.
  • This non-return valve prevents pumped fluid from entering one pump into the pressure side of the other pump, thus creating unnecessary hydraulic resistance. Rather, the non-return valve 3a directs the flow of the two pumps 2a, 2b in the pressure line. 5
  • Each pump 2a, 2b is associated with a pump electronics 6, which controls the electric motor drive unit of the pump 2a, 2b.
  • the pump electronics 6 is connected to an operating voltage and energized the respective electric motor by means of a frequency converter.
  • the frequency converter is controlled by a pulse width modulated (PWM) signal from a microprocessor of the pump electronics in response to a speed reference is produced.
  • PWM pulse width modulated
  • This speed setpoint is output by a controller, which is also part of the pump electronics, in particular implemented in the microprocessor of the electronics.
  • This controller is superior to the method according to the invention and regulates a pump 2a, 2b according to a control characteristic which can be specified at the respective pump electronics 6.
  • the pressure generated by a pump 2a, 2b is regulated, wherein the pumps 2a, 2b are set up for measuring the differential pressure between the suction side and the pressure side.
  • the pump unit 1 may also be pressure-controlled, wherein only the control of one of the two pumps 2a, 2b is needed.
  • the two pump electronics 6 of the pumps 2a, 2b are connected in parallel via a control line 8.
  • the pump electronics 6 of the second pump 2b can receive the same control signal for their frequency converter via this control line 8, which is output by the pump electronics 6 of the first pump 2a.
  • the first pump 2a thus functions, together with its regulating / control electronics 6, as a type of master, whereas the second pump 2b is controlled with its regulating / control electronics 6 as a type of slave.
  • a synchronous operation of the two electromotive drive units of the first pump 2a and the second pump 2b is achieved.
  • the pump electronics 6 of the second pump 2b is completely identical in design to the pump electronics 6 of the first pump 2a and can if necessary control the second pump 2b completely independently of the pump electronics 6 of the first pump 2a.
  • FIG. 2 shows an exemplary second embodiment of the pump unit 1 according to the invention with a plurality of parallel operating pumps 2a, 2b. Of this variety, however, only three pumps in the FIG. 2 shown. In this case, two pumps 2a act as synchronously running base load pumps and a pump 2b as a peak load pump. All pumps are connected to a common suction line 4 and open into a common pressure line 5. Between each pump 2a, 2b and the pressure line 5, a check valve 3 is arranged, which like the non-return valve 3a in FIG. 1 each prevents that under pressure standing pumped medium enters the pressure-side region of a less pumping or pump switched off.
  • each pump 2a, 2b is equipped with a pump electronics 6, which can control the corresponding pump 2a, 2b completely self-sufficient, that can energize the electric motor drive unit such that the pump 2a, 2b is controlled on a predetermined control characteristic.
  • the pump electronics 6 according to FIG. 2 are therefore identical to the pump electronics 6 in FIG. 1 , Basically, the pump electronics 6 can be connected to each other via control lines, not shown, and implement control technology, a master / slave arrangement in this second embodiment.
  • a higher-level central control unit 7 is shown, with which the individual pump electronics 6 are connected via a respective control line 9. About this central control unit 7, the rotational speeds of the individual pumps 2a, 2b of the pump unit 1 in FIG. 2 specified.
  • Pump units 1 shown are preferably used as circulation pumps in heating systems or as printing stations for fresh water delivery.
  • the first pump 2a is used to operate the base load and the second pump 2b to operate the peak load.
  • the first pump 2a is referred to in the context of the invention as a base load pump, whereas the second pump 2b is referred to as a peak load pump.
  • the peak load pump 2 b is required on the one hand to cover a flow requirement that can not be met by the base load pump alone. However, it is also operated synchronously to the base load pump in an area of the characteristic field in which the synchronous operation of both pumps is energetically more favorable than the exclusive operation of the base-load pump.
  • the inventive method can easily on a multi-pump unit according to FIG. 2 can be extended by the base load pump 2a and a connected peak load pump 2a control technology together as a base load pump 2a are considered, to which a further pump 2b, namely the new peak load pump 2b is connected.
  • FIG. 3 shows the superordinate sequence of the method according to the invention. The method is performed immediately when commissioning the pump unit 1 and learns to himself, when it is energetically cheaper to operate only the base load pump or when a synchronous operation of base load and peak load pump 2a, 2b is energetically cheaper.
  • an upper limit value n_o and a lower limit value n_u are defined, and values are given to these limit values in a step 12 labeled "reset".
  • the upper limit n_o is set equal to the maximum speed n_max of the base load pump 2a
  • the lower limit n_u is set equal to the minimum speed n_min of the base load pump 2a. Since the two pumps 2a, 2b are designed to be identical, these limits also correspond to those of the peak load pump 2b and the double pump unit 1 in synchronous operation.
  • n_u_GLP defines a base load reference value of the rotational speed. This reference value is occupied in the course of the process with that speed n_GLP of the base load pump 2a which is applied to the base load pump 2a when the base load operation, i. is transferred to the operation with only the base load pump 2a.
  • This speed value then serves as a reference to the current speed n_GLP of the base-load pump 2 a, by means of which an abnormal speed increase of the base-load pump 2 a can be ascertained. This will be explained in more detail below.
  • FIG. 3 summarized by the APL (Adaptive Peak Load) designated block 20, its implementation FIG. 4 shows and explained below.
  • APL 20 implements a power control of the pump set 1 with dynamic threshold adjustment.
  • a new setpoint presetting 14 i. If the control characteristic changes, the process is restarted and new limit values n_u, n_o, n_u_GLP are set for this control characteristic.
  • the previously determined limit values relative to the original control characteristic i. the original setpoint default are stored so that they can be reused when returning to the previous setpoint setpoint.
  • a new setpoint specification 14 does not mean that the previously determined limit values are deleted. Rather, new limit values n_u, n_o, n_u_GLP are only set when a control characteristic is set in the pump unit 1, which has never been set before. If you change to a previously set characteristic, the limit values already determined for this characteristic will continue to be used. If, on the other hand, there is no change in the control characteristic during the execution of the steps of the APL block 20, these APL steps are repeated cyclically.
  • FIG. 4 graphically illustrates the individual steps of the APL block 20 in FIG FIG. 3 of the method according to the invention in a logical flowchart.
  • the method begins with a synchronous operation 21 of the pump unit 1, in which the pump electronics 6 of the base load pump 2a and the peak load pump 2b regulate them such that the speed of the base load pump n_GLP and the speed of the peak load pump n_SLP are identical and correspond to a predetermined synchronous speed n_sync.
  • the synchronous operation is in FIG. 4 characterized by the block 21.
  • the synchronous speed n_sync is specified by the higher-level controller, which adjusts the pump unit 1 in such a way that the differential pressure ⁇ p or the delivery height H of the pump unit 1 in accordance with the predetermined volume flow Q given by the hydraulic system in which the pump unit 1 is integrated Control characteristic holds.
  • the speed n_GLP of the base-load pump 2a should increase only slightly in order to compensate for the reduced volume flow due to the elimination of the peak load pump 2b. However, should the speed n_GLP of the base-load pump 2a increase to the maximum speed n_max, which is subsequently checked in step 37, the lower limit value n_u has been set incorrectly. It is therefore reset to the initial value in the subsequent step 38, i. reset to the minimum speed n_min. In this case, the peak load pump 2 b is immediately connected again and the pump unit 1 is operated in synchronous operation 21.
  • FIG. 5 shows a schematic representation of the family of characteristics of a double pump 1 according to FIG. 1 ,
  • the characteristic field is formed by a plurality of characteristic curves 44 of constant speed and pipe network parabolas 43 whose pitch is predetermined by the pipe network resistance of the hydraulic system in which the pump unit 1 is integrated.
  • the characteristic field is limited to the top by a maximum characteristic 41 of the pump unit 1.
  • This characteristic 41 corresponds to the operating points of the pump unit 1, which can be reached at maximum synchronous speed of the two individual pumps 2a, 2b.
  • the characteristic indicated by the reference numeral 18 is the maximum characteristic of one of the pump 2a, 2b, in particular the base load pump 2a.
  • This characteristic curve 18 identifies all operating points that can be reached during exclusive operation of the base-load pump 2 a at the maximum rotational speed n_max. Between the maximum characteristic 41 of the pump unit 1 and the maximum characteristic curve 18 of the basic load pump 2a is the peak load region 15. Thus, the pump unit 1 can reach an operating point within this peak load range 15, the operation of base load pump 2a and peak load pump 2b is required.
  • the characteristic field is limited by a minimum characteristic 42 of the base-load pump 2 a. Between the minimum characteristic 42 and the maximum characteristic 18, each operating point of the pump unit 1 can be achieved exclusively by the base-load pump 2 a.
  • This intermediate region is divided into the base load region 17, in which it is energetically more favorable to operate only the base load pump 2a, and an efficiency-optimized region 16, in which the pump unit 1 receives less power when base-load pump 2a and peak load pump 2b are operated simultaneously, in particular synchronously , against an exclusive operation of the base load pump 2a.
  • This efficiency-optimized region 16 is substantially in the range of low to medium volume flows Q at low to medium head H.
  • the transition between the base load region 17 and the efficiency-optimized region 16 is characterized by a boundary line 40, whose position has been found by measuring the characteristic field on the test bench according to the prior art. According to the invention, however, the position of this boundary line 14 is found out with increasing accuracy during operation of the pump unit 1.
  • FIG. 6 Referenced.
  • the pump unit 1 is first controlled according to a first control characteristic 19, on which the pressure ⁇ p of the pump unit 1 or the delivery height H is kept constant over the volume flow Q.
  • a first control characteristic 19 on which the pressure ⁇ p of the pump unit 1 or the delivery height H is kept constant over the volume flow Q.
  • n_u and the upper limit value n_o are plotted. It is first assumed that after the commissioning of the pump unit 1 and the set synchronous operation 21, a first Operating point 11 sets, which is in the base load range 17. This is determined by the method as follows.
  • step 22 With reference to FIG. 4 was first determined in step 22 that the currently applied synchronous speed in the operating point 11 is not less than the lower limit n_u. It is then checked in step 23 whether the current synchronous speed n_sync is smaller than the upper limit value n_o. This is the case at the operating point 11 because the upper limit n_o has been set equal to the maximum speed n_max of the base load pump 2a. In step 23 it is also checked whether the synchronous speed n_sync is less than the maximum speed n_max. Since the method according to the invention has not yet set a new upper limit value n_o at this point, the aforementioned second condition is identical to the first one. It therefore only becomes significant if, in the course of the method, the upper limit n_o is set to a value below the maximum speed n_max.
  • step 23 For the operating point 11 in FIG. 6 the conditions tested in step 23 are met. This is followed by a storage of the current synchronous speed n_sync as reference speed n_ref, step 24a. Subsequently, the total electrical power P_ ⁇ is determined and stored in step 24b as a reference power P_ref. Thereafter, in step 25, the speed n_SLP of the peak load pump 2b is reduced, for example, by 100 rpm. As a result, the flow rate of the peak load pump 2b is reduced. The two pumps 2a, 2b are no longer operated synchronously. The reaction of the pump unit 1 to this speed reduction will now be analyzed.
  • the higher-level speed controller now controls the resulting from the speed reduction of the peak load pump pressure drop of the pump unit 1, characterized in that the speed of the base-load pump is increased.
  • any existing valves in the hydraulic system for example, thermostatic valves readjust.
  • a wait time t_wait is waited for in step 35. This is between one and 20 s, preferably between 5 and 15 s, in particular about 10 s, and it can be chosen in particular as a product of the settling time of the pressure regulator and a factor which is preferably between two and five. Wait a counter for the waiting time can be set to zero immediately after a speed reduction in step 25 and then counted up numerically. Only after expiry of the waiting time t_wait is it checked how the pump unit 1 reacts to the speed reduction of the peak load pump 2b in step 25.
  • step 26 it is first checked in step 26 whether the rotational speed n_GLP of the base-load pump 2a reaches or exceeds its maximum value n_max due to the speed reduction of the peak load pump 2b. If this were the case, then the current operating point 11 would be in the peak load range 15. However, this is not the case here.
  • step 26 it is checked in step 26 as an alternative condition whether the now adjusting electrical power consumption P_GLP of the base load pump 2 a rises above the stored power reference value P_ref. If this were the case at the operating point 11, it would either be in the efficiency-optimized range 16 or in the peak load range 15. If the speed condition n_GLP ⁇ n_max is checked before the power condition P_GLP> P_ref and the speed condition is not satisfied, then the power condition would have been checked in that the operating point lies in the efficiency-optimized region 16.
  • step 26 a hierarchical examination of the two conditions in step 26 is not absolutely necessary, since both in the case of performance of the performance condition and in the case of meeting the speed condition in each synchronous operation is transferred, step 29.
  • the procedural response to the occurrence of one of these conditions is therefore the same.
  • step 27 If the power P_GLP of the base-load pump 2 a still changes after the speed reduction, no concrete statement can yet be made as to whether or not the operating point 11 lies in the base load range 17. It then proceeds from step 27 to the next step 28.
  • step 28 Since the peak load pump 2b is given a specific speed by the method according to the invention, only the base load pump 2a remains under the controlled influence of the superordinate pressure regulator so that it downshifts the power of the base-load pump 2a. Whether this is the case is checked in step 28. If this case occurs, then the operating point 11 has changed and a statement about its original position can not be made at this point. From step 28, therefore, the method according to the invention returns to synchronous operation 21, from where it begins anew with the changed operating point.
  • step 28 if the condition in step 28 is not met, the power of the base-load pump 2a either increases or fluctuates as a result of the volume flow transfer, so that no concrete statement can be made about the operating point.
  • step 25 A further speed reduction of the peak load pump 2b is then performed in step 25 and the system response is again awaited. Subsequently, the conditions 26, 27 and 28 are checked again.
  • step 32a the previously stored reference speed r_ref, which is associated with the operating point 11, is stored as the lower limit n_u, since it is now clear that the operating point 11 is in the base load range 17.
  • the peak load pump 2b is then turned off, step 32b. Since in this way the rotational speed n_GLP of the base-load pump 2 a can change again, it makes sense to provide here a further waiting time, which in FIG. 4 but not taken into account.
  • the current speed n_GLP of the base load pump 2 a including an added offset is stored as a base load reference value n_u_GLP, step 32 c.
  • the pump unit 1 is now operated in the base load mode 33, in which the peak load pump 2b is turned off, ie their speed n_SLP is zero, whereas the base load pump 2a continues to be operated at a non-zero speed n_GLP. This is in block 33 in FIG. 4 shown.
  • the rotational speed n_GLP of the base-load pump 2a is constantly checked. If it rises above the stored base load reference value n_u_GLP, it returns directly to synchronous mode 21. For safety reasons, it is also checked in condition 34 for the case of an incorrectly set base load reference value n_u_GLP whether the speed of the base-load pump n_GLP rises above its maximum speed n_max. If this is the case, is also transferred to the synchronous mode 21.
  • Fig. 7 shows that the lower limit n_u is now set to the speed value that existed at the first operating point 11 before the volume flow reduction of the second pump 2b. This means that every other operating point has one speed is also in the base load range 17 below the new lower limit n_u. The area below the lower limit n_u is in FIG. 7 therefore marked hatched.
  • FIG. 7 assumed that sets an operating point in the peak load range 15 as the second operating point 13.
  • the speed n_GLP of the base-load pump will increase considerably compared to the base-load reference value n_u_GLP, in particular increase above the maximum speed n_max.
  • the in step 34 in FIG. 4 mentioned and constantly checked conditions are therefore met and it is transferred to the synchronous mode 21.
  • the then adjusting synchronous speed n_sync must necessarily be above the previously stored in the operating point 11 synchronous speed, so that the condition 22 in FIG. 4 is not fulfilled. Since the upper limit value n_o still corresponds to the maximum synchronous speed value n_max, the condition tested in step 23 or the two conditions mentioned there are fulfilled.
  • the current synchronous speed n_sync is therefore stored again as a speed reference value n_ref, step 24a, and the electrical power P_ ⁇ recorded by the pump unit is determined and stored as reference power P_ref, step 24b.
  • the speed n_SLP of the peak load pump 2b is reduced, step 25, and the reaction of the pump set 1 to this speed reduction is awaited, step 35, and analyzed.
  • step 26 The reduction of the rotational speed n_SLP will cause the rotational speed n_GLP of the base-load pump 2a to reach its maximum value n_max because the operating point 13 conditions a volumetric flow Q which lies beyond the maximum characteristic curve 18 of the basic-load pump 2a. For this reason, the condition in step 26 will be satisfied after a certain time, so that the synchronous operation is returned, step 29 in FIG. 4 ,
  • the new operating point 13 is in the peak load range 15, so that the synchronous speed stored as reference speed n_ref n_sync can be set as the upper limit n_o, step 31.
  • the speed of the base load pump n_GLP returns to its original value, namely to the original synchronous speed n_sync.
  • step 30 in FIG. 4 checked. Only if this is the case, the reference value n_ref is set as upper limit n_o. Otherwise, the current operating point has changed again, so that a clear statement about its location is not possible.
  • the procedure is then continued in synchronous mode 21. However, for the case illustrated purely by way of example, the operating point 13 remains unchanged, so that the reference value n_ref is set as upper limit n_o. This is in FIG. 8 shown.
  • FIG. 11 further illustrates that synchronous speeds above the upper limit n_o belong to operating points in which both the base load pump 2 a and the peak load pump 2 b should be operated. Furthermore, in FIG. 8 a third operating point 45 assumed by way of example, which is now in the efficiency-optimized region 16.
  • a synchronous rotational speed n_sync will again set above the lower limit n_u with the new operating point 45, so that the condition in step 22 in FIG. 4 is not fulfilled.
  • both are met in step 23 to be tested conditions so that the current synchronous speed n_sync can be stored again as a reference value n_ref, step 24.
  • the currently recorded electrical power P_ ⁇ the pump unit 1 is again stored as a reference power P_ref, step 24b.
  • the speed n_SLP of the peak load pump 2b is again reduced, step 25, and waited until the higher-level pressure regulator has corrected.
  • step 26 Since the new operating point 47 is in the base load range 17, none of the conditions tested in step 26 will be met. This means that the base-load pump 2a neither reaches its maximum speed n_max nor achieves a power consumption which is above the reference power P_ref due to the speed reduction of the peak load pump 2b. The speed reduction of the peak load pump 2b will cause the power P_GLP picked up by the base load pump 2a to initially increase but then reach a saturation value when the base load pump 2a has almost completely taken over the flow rate of the peak load pump 2b. Since the power P_GLP of the base-load pump no longer changes significantly in this case, the condition in step 27 is fulfilled.
  • the reference speed n_ref is then set as the new lower limit n_u, step 32a, the peak load pump 2b turned off, step 32b, and the then present actual speed n_GLP of the base load pump 2a plus an offset set as the new base load reference value n_u_GLP, step 32c.
  • the pump unit 1 is then operated in the base load mode 33, in which the peak load pump 2 a is turned off and the pump unit 1 is controlled exclusively with the base load pump 2 a on the set control characteristic 19.
  • FIG. 11 now the change to a new constant control characteristic 40 is illustrated.
  • a new lower limit n_u and a new upper limit n_o are set, which are assigned a minimum value or maximum value for the rotational speeds.
  • n_u is assigned a minimum value or maximum value for the rotational speeds.
  • n_o is again a new, fifth operating point 48 located, which is in the base load range 17.
  • the method will now be described in accordance with the above-described steps in FIG. 4 as before on the basis of Figures 6-10 explained. Based on FIG. 11 It is still clear that the limit values n_u, n_o determined for the previous control characteristic 19 remain, so that in the case of a return to the original control characteristic 19 these limit values n_u, n_o can be reused.
  • FIG. 12 illustrates the application of the method according to the invention with a further control characteristic 39, according to which the delivery pressure ⁇ p of the pump unit 1 is controlled linearly via the volume flow Q.
  • FIG. 12 are already shown adjusted values for the lower limit n_u and the upper limit n_o, which have been determined during operation. Between the two limits, the boundary line 40 runs.
  • FIG. 13 illustrates the graph of the measured values for the speed n_setpoint specified for the peak load pump 2b, for the total output P1_Sum of the pump set, for the power P1_MA of the base load pump and for the power P1_SL of the peak load pump, for a head H of 15 m and a flow Q of 55 m 3 / H.
  • the speed n_soll of the peak load pump 2b is reduced by 100 rpm.
  • the power consumption P1_SL of the peak load pump 2b decreases significantly, whereas the power P1_MA of the base load pump 2a increases by a higher amount.
  • the power P1_MA the base load pump 2a has reached a value of about 4000 watts.
  • a subsequent further speed reduction of 100 rpm has a reduction in the power P1_SL received by the peak load pump 2b, it does not change the power consumption P1_MA of the base load pump 2a.
  • FIG. 13 shows that this total power is always above the curve of the power P1_MA the base load pump 2a. This means that the operating point from which in FIG. 13 is assumed before the speed reduction is in the base load range 17, in which the power consumption of the base load pump 2a does not increase above the previously recorded in synchronous operation 21 before the speed reduction power P1_Sum the total unit.
  • FIG. 13 therefore illustrates the physical quantities on the pump set 1, when an operating case according to FIG. 6 is present.

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Claims (22)

  1. Procédé de fonctionnement d'un agrégat de pompes (1) avec au moins une première pompe (2a) desservant une charge de base et au moins une deuxième pompe (2b) desservant une charge de pointe, qui est au besoin connectée et utilisée en parallèle à ladite au moins une première pompe (2a), dans lequel l'agrégat de pompes (1) est régulé sur une caractéristique de réglage prédéterminée (19, 39), de telle manière que la puissance consommée soit minimale, caractérisé en ce que l'on fait fonctionner l'agrégat de pompes (1) en fonction d'une valeur limite supérieure et d'une valeur limite inférieure (n_o, n_u) d'une grandeur de fonctionnement (n_sync) soit avec au moins deux pompes (2a, 2b) soit avec au moins une pompe déconnectée (2b), dans lequel, à partir d'un fonctionnement synchrone (21) des pompes (2a, 2b) en un point de fonctionnement (11, 13) dans lequel les pompes (2a, 2b) fonctionnent avec la même vitesse de rotation (n_sync) et/ou la même puissance,
    a. dans une première étape (24a), on mémorise la valeur d'au moins une grandeur de fonctionnement (n_sync) de l'agrégat de pompes (1) comme valeur de référence (n_ref),
    b. dans une deuxième étape (25), on réduit le flux volumique refoulé par la deuxième pompe (2b),
    c. dans une troisième étape (26, 27), on opère une association du point de fonctionnement (11, 13) à une plage de charge (15, 16, 17) en fonction de la réaction de la première pompe régulée (2a), et
    d. dans une quatrième étape (31, 32a), on remplace la valeur limite supérieure ou inférieure (n_o, n_u) par la valeur de référence (n_ref).
  2. Procédé selon la revendication 1, caractérisé en ce que la grandeur de fonctionnement est la vitesse de rotation synchrone (n_sync) de l'agrégat de pompes (1), que l'on mémorise comme vitesse de rotation de référence (n_ref).
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que l'on détermine la puissance (P_Σ) consommée par l'agrégat de pompes (1) dans le fonctionnement synchrone (21) et on la mémorise comme puissance de référence (P_ref).
  4. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'on mémorise (31) la valeur de référence (n_ref), en particulier la vitesse de rotation de référence (n_ref) comme une valeur limite supérieure (n_o), en particulier une valeur limite de vitesse de rotation (n_o) , lorsqu'après la réduction du flux volumique (25), au moins une première condition (26) est remplie, qui est associée à une des plages de charge (15, 16) : plage de charge de pointe (15) ou plage à rendement optimisé (16) .
  5. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'on mémorise (32a) la valeur de référence (n_ref), en particulier la vitesse de rotation de référence (n_ref), comme une valeur limite inférieure (n_u), en particulier une valeur limite de vitesse de rotation (n_u), lorsqu'au moins une deuxième condition (27) est remplie, qui est associée à la plage de charge de base (17).
  6. Procédé selon les revendications 4 et 5, caractérisé en ce que l'on fait fonctionner l'agrégat de pompes (1) à un point de fonctionnement (11) avec une vitesse de rotation synchrone (n_sync) égale ou supérieure à la valeur limite supérieure (n_o) avec au moins deux pompes (2a, 2b) et égale ou inférieure à la valeur limite inférieure (n_u) avec au moins une pompe déconnectée (2b).
  7. Procédé selon les revendications 4 et 5 ou la revendication 6, caractérisé en ce que l'agrégat de pompes (1) en un point de fonctionnement (13) avec une vitesse de rotation synchrone (n_sync) entre la valeur limite supérieure (n_o) et la valeur limite inférieure (n_u), on répète les étapes a. à d. en partant d'un fonctionnement synchrone (21) des pompes (2a, 2b).
  8. Procédé selon l'une quelconque des revendications précédentes 4 à 7, caractérisé en ce que l'on mémorise les valeurs limites (n_o, n_u) associées à l'ancienne caractéristique de réglage (19, 39, 46) lors d'un changement de cette caractéristique de réglage (19, 39, 46), et on utilise pour la nouvelle caractéristique de réglage (19, 39, 46) une nouvelle valeur limite supérieure et inférieure (n_o, n_u).
  9. Procédé selon l'une quelconque des revendications 4 à 8, caractérisé en ce que la première condition (26) est remplie, lorsque la vitesse de rotation (n_GLP) de la première pompe (2a) atteint ou dépasse une vitesse de rotation maximale (n_max), ou lorsque la consommation de puissance (P_GLP) de la première pompe (2a) dépasse la puissance de référence (P_ref).
  10. Procédé selon l'une quelconque des revendications 5 à 9, caractérisé en ce que la deuxième condition (26) est remplie, lorsque la consommation de puissance (P_GLP) de la première pompe (2a) reste en moyenne essentiellement égale, ou lorsque la vitesse de rotation (n_SLP) de la deuxième pompe (2b) atteint ou descend en dessous d'une valeur minimale.
  11. Procédé selon la revendication 4 et l'une quelconque des revendications 5 à 10, caractérisé en ce que la deuxième condition (27) n'est vérifiée que lorsque la première condition (26) n'est pas remplie.
  12. Procédé selon l'une quelconque des revendications 5 à 11, caractérisé en ce que, lors de la mémorisation (32a) de la valeur limite inférieure (n_u), on mémorise (32c) la valeur d'une grandeur de fonctionnement (n_GLP) de la première pompe (2a) comme valeur de référence de la charge de base (n_u_GLP).
  13. Procédé selon la revendication 12, caractérisé en ce que l'on passe du fonctionnement (33) avec au moins une pompe déconnectée (2b) à un fonctionnement synchrone (21) avec au moins deux pompes (2a, 2b), lorsque la valeur instantanée de la grandeur de fonctionnement (n_GLP) de la première pompe (2a) grimpe au-dessus de la valeur de référence de la charge de base (n_u_GLP) ou est égale ou supérieure à une valeur maximale (n_max) de cette grandeur de fonctionnement (n_GLP).
  14. Procédé selon la revendication 12 ou 13, caractérisé en ce que l'on utilise comme grandeur de fonctionnement de la première pompe (2a) sa vitesse de rotation (n_GLP).
  15. Procédé selon la revendication 12, 13 ou 14, caractérisé en ce que l'on ajoute (32c) un décalage à la valeur de référence de la charge de base (n_u).
  16. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'après la réduction de flux volumique (25), on revient à un fonctionnement synchrone (21) lorsque, comme troisième condition (28), la consommation de puissance (P_GLP) de la première pompe (2a) baisse.
  17. Procédé selon l'une quelconque des revendications précédentes 4 à 16, caractérisé en ce que l'on ne vérifie qu'après un temps d'attente (t_warten) si au moins une des conditions (26, 27, 28) est vérifiée.
  18. Procédé selon l'une quelconque des revendications précédentes 4 à 17, caractérisé en ce que l'on réduit encore (25) le flux volumique de la deuxième pompe (2b), lorsqu'aucune des conditions (26, 27, 28) n'est remplie.
  19. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'on passe à un fonctionnement synchrone (21), lorsque la vitesse de rotation (n_GLP) de la première pompe (2a) atteint ou dépasse une valeur maximale (n_max), ou en ce que l'on revient immédiatement à un fonctionnement synchrone (29) lorsque la première condition (26) est remplie et on ne mémorise (31) la valeur de référence (n_ref) comme valeur limite supérieure (n_o) que lorsque, après le retour, l'état de fonctionnement d'avant la réduction de flux volumique se rétablit (30).
  20. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que l'on ramène (38) la valeur limite inférieure (n_u) à une valeur minimale et on revient à un fonctionnement synchrone (21), lorsque la première pompe (2a) atteint un état de fonctionnement inacceptable, en particulier atteint ou dépasse une vitesse de rotation maximale (n_max).
  21. Programme informatique contenant des instructions pour l'exécution du procédé selon l'une quelconque des revendications précédentes, lorsqu'il est exécuté sur un micro-ordinateur d'une électronique de commande (6, 6a, 6b).
  22. Agrégat de pompes (1) avec au moins une première pompe (2a) desservant une charge de base et au moins une deuxième pompe (2b) desservant une charge de pointe, qui est au besoin connectée et qui peut être utilisée en parallèle à ladite au moins une première pompe (2a), dans lequel l'agrégat de pompes (1) peut être régulé sur une caractéristique de réglage prédéterminée (19, 39), de telle manière que la puissance consommée soit minimale, caractérisé en ce qu'il présente une électronique de commande (6, 6a, 6b), qui est conçue pour l'exécution du procédé selon l'une quelconque des revendications 1 à 20.
EP11009716.9A 2010-12-23 2011-12-08 Procédé de fonctionnement d'un agrégat de pompes doubles ou multipompes Active EP2469094B1 (fr)

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