EP2940309B2 - Procédé de réglage d'un système de pompe et système de pompe réglé - Google Patents

Procédé de réglage d'un système de pompe et système de pompe réglé Download PDF

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Publication number
EP2940309B2
EP2940309B2 EP15000541.1A EP15000541A EP2940309B2 EP 2940309 B2 EP2940309 B2 EP 2940309B2 EP 15000541 A EP15000541 A EP 15000541A EP 2940309 B2 EP2940309 B2 EP 2940309B2
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Prior art keywords
pump
speed
power input
rotational speed
pumps
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German (de)
English (en)
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EP2940309B1 (fr
EP2940309A1 (fr
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Joachim Fehr
Thomas Tillmann
Carsten Diederichs
Renato Ortiz
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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
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F04D13/14—Combinations of two or more pumps the pumps being all of centrifugal type
    • 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
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0016—Control, e.g. regulation, of pumps, pumping installations or systems by using valves mixing-reversing- or deviation valves
    • 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
    • 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 controlling a double pump which has two hydraulically parallel operated centrifugal pumps which are arranged in a common pump housing and are each driven by speed-controlled, electric motor drive units.
  • the invention further relates to a double pump for applying the method.
  • centrifugal pumps operated hydraulically in parallel are known. Due to the parallel operation, they pump into a common pressure line.
  • Each of these pumps usually consists of a pump unit, an electric motor that drives it, which is usually preceded by a frequency converter, and control electronics that typically regulate the speed of the centrifugal pump according to a predetermined control curve.
  • So-called double pumps are also known, in which two centrifugal pumps are arranged in a single pump housing, as described in the European patent application EP 0 735 273 A1 is described
  • German patent application DE 3918246 A1 discloses a pump system with several pumps, in which a second or further pump is switched on and off depending on the performance of a first pump.
  • the second or further pump has a fixed delivery capacity and is only switched on or off as required.
  • the pump system here does not consist of a double pump with a common housing but of independent pump units.
  • This phenomenon is particularly pronounced when the centrifugal pumps discharge the pressure line via an uncontrolled valve that has a valve flap.
  • this flap is positioned approximately centrally in relation to the flow cross-sections at the respective pump outlet, so that the effective flow cross-sections at the outlets of the two pumps are the same. If the flow rates are slightly unequal, the flap appears to be fully open for one pump, i.e. it only creates a small hydraulic resistance. For the other pump, however, the off-center valve flap creates a partially closed valve, i.e. it creates a high hydraulic resistance against which it discharges. This resistance causes the aforementioned further reduction in the delivery capacity of this pump.
  • this other pump consumes unnecessary energy in supposedly synchronous operation because it pumps against the partially closed valve flap.
  • EP1614903A1 does mention this problem of hydraulic asymmetry in double pumps, but to solve it it only teaches the use of a control system that is permanently adapted to the corresponding hydraulic system, without explaining how this adaptation should be carried out. There is no active, automatic adaptation during operation. Different parameters for the control of the hydraulic system are simply programmed at the factory or during installation.
  • the international publication WO 2009/079447 A1 addresses the problem of the different hydraulic properties of the centrifugal pumps in a double and multi-pump system. It solves this by balancing the torque between the pumps in order to achieve the same flow rates.
  • the tables in the publication show that, in order to achieve the control target of identical torques, different speeds are set for the centrifugal pumps.
  • the electrical power consumed by the centrifugal pumps is also different.
  • the US application US 2009/0287357 A1 describes a pump control system with a large number of different variable speed pumps, a system-wide first PID control to increase or decrease the speed of all pumps and a pump-specific second PID control that adjusts the speed of each pump to equalize the load profiles of the individual pumps.
  • the load of each pump is recorded, an average value is determined from this and the speed of the pump whose load is below the average is increased so that the pumps all carry the same load.
  • the Canadian patent application CA02831759A1 also describes a system of several parallel pumps, which are controlled in such a way that certain performance characteristics are present, such as reduced wear and/or power consumption. In a variant with three pumps, it is described that, depending on requirements, only one pump, two or all three pumps are operated simultaneously, whereby with two or three pumps an even distribution of the volume flow is carried out.
  • the CA02831759A1 a standardisation of the power consumption of the pumps or their speeds compared to the power consumption ratio, without going into further detail.
  • Hyamaster ® SPS from KSB Aktiengesellschaft, 67225 Frankenthal, Johann-Klein-Str. 9, which has a stepless speed adjustment via frequency converter for all pump drives with three-phase motors, is known to adjust the flow rate in such a way that the speed of the pump with the lower power is increased depending on the power consumption of the frequency converter until all pumps are operating at the same power.
  • the object of the present invention is to provide an alternative method for controlling a pump system of two hydraulically coupled centrifugal pumps, which instead of a purely speed-synchronous operation sets a predetermined ratio of the delivery rates of the centrifugal pumps, in particular a substantially equal delivery rate, in order to operate the pump system in an energy-efficient manner. Furthermore, it is to provide a corresponding pump system for carrying out the method.
  • a method for controlling a pump system in the form of a double pump, which has two hydraulically parallel-operated centrifugal pumps, which are arranged in a common pump housing and are each driven by speed-controlled, electromotive drive units, in which the determined electrical power consumption of one of the centrifugal pumps is compared with the determined power consumption of the other centrifugal pump, and depending on the result of this power comparison, the speed of at least one of these centrifugal pumps is adjusted such that the electrical power consumption of the centrifugal pumps reaches a predetermined ratio.
  • the core idea of the present invention is to adapt the centrifugal pumps, starting from a speed-synchronous operation in which the delivery capacity of one of the centrifugal pumps is impaired due to the delivery capacity of the other pump, in such a way that the impairment of one centrifugal pump is reduced. This can be done in various ways.
  • the speed of at least one of the centrifugal pumps can be adjusted in such a way that the electrical power consumption of the centrifugal pumps is equalized.
  • the control is carried out in such a way that the power consumption reaches a predetermined ratio of 1.
  • a ratio in the sense of the invention can not only be a geometric ratio that describes the quotient of the power consumption, but also an arithmetric ratio that describes the difference in the power consumption.
  • equalizing the electrical power consumption of the centrifugal pumps means that the control is carried out to a difference of zero between the power consumptions.
  • Matching the electrical power consumption to each other means that they essentially consume the same electrical power, at least on average.
  • the ratio can basically be fixed. However, it is advantageous to choose the ratio depending on the operating point, so that the ratio is defined, for example, depending on the volume flow delivered by the pump system or the differential pressure.
  • the ratio can become smaller as the volume flow increases, i.e. it can be smaller for low volume flows than for high volume flows, because the hydraulic differences of the centrifugal pumps are more noticeable at low volume flows than at high volume flows.
  • the centrifugal pumps deliver into a common pressure line, with which they are connected to one another via an uncontrolled valve that has at least one actuating device.
  • the actuating device can be a valve flap or a ball valve.
  • the position of the actuating device depends on the delivery pressure or flow rate of both centrifugal pumps. This means that the flow rate of one centrifugal pump determines, or at least co-determines, the degree to which the valve for the other centrifugal pump opens.
  • the proposed method enables the flow rates to be balanced and the power consumption to be symmetrized, provided that the ratio is regulated to 1.
  • the control according to the invention takes place dynamically during operation of the pump system.
  • the method can be downstream of a characteristic curve control of the pump system, which ideally outputs a synchronous speed setpoint for all centrifugal pumps. This means that the method can be used universally for any double pump with two centrifugal pumps.
  • the two centrifugal pumps are housed in a common pump housing. This means that their impellers each rotate in a pump chamber, which structurally share a single housing. If a valve of the type described above is present, this can then be part of the pump housing or be arranged in it.
  • the two drive units can be structurally identical. This means that they do not differ significantly in their electromechanical properties, particularly in terms of speed and torque with identical current supply. However, it is also possible and conceivable for individual applications that different drive units, particularly with different power and/or size, are used for the pump system. For example, in a double pump unit, one of the two drive units can be more powerful than the other drive unit.
  • the centrifugal pumps do not necessarily have to be identical either. Rather, they can have different impellers.
  • the ratio can be significantly smaller than for identical drive units or centrifugal pumps, for example between 0.5 and 0.85.
  • the speed of the centrifugal pumps is controlled by a characteristic curve control which outputs a synchronous speed setpoint for all centrifugal pumps. This enables the operating point of the pump system to be adapted to the current operating state of the hydraulic system supplied by the pump system.
  • the speed setpoint for at least one of the centrifugal pumps is then adjusted downstream of this characteristic curve control depending on the result of the performance comparison.
  • the speed is only suitably adjusted when the power difference between the drive units exceeds a predetermined limit value.
  • a limit value By using a limit value, a hysteresis is formed which suppresses constant regulation in the event of small power differences.
  • the limit value can be between 1% and 10%, for example 2% of the maximum power of the drive units. According to a further development, different limit values can be used for positive and negative power differences.
  • a first limit value can be used and in the case of a negative power difference between one and the other centrifugal pump unit, a second limit value can be used. If these limit values are the same, a symmetrical hysteresis window results; if the limit values are unequal, an asymmetrical hysteresis window results. Both limit values can be, for example, between 1% and 10%, preferably about 2% of the maximum power of the drive units.
  • the pump system can be controlled in such a way that the speed of one drive unit is reduced relative to the speed of the other drive unit and/or the speed of the other drive unit is increased relative to the speed of one drive unit if the power consumed by one drive unit is higher, in particular higher by the first limit value, than the power consumed by the other drive unit.
  • the speed of one drive unit can be increased relative to the speed of the other drive unit and/or the speed of the other drive unit can be reduced relative to the speed of one drive unit if the power consumed by one drive unit is lower, in particular lower by the second limit value, than the power consumed by the other drive unit.
  • the speed can therefore be adjusted in three different ways. It can either be done only on one centrifugal pump, only on the other centrifugal pump, or on both centrifugal pumps at the same time, with the adjustment in the latter case taking place in the opposite direction.
  • the speed is only adjusted up to a maximum value.
  • This maximum value can be specified in relative or absolute terms.
  • the speed can be adjusted by a maximum of 2% to 6% of the nominal speed of the centrifugal pumps. 2% to 6% means that for centrifugal pumps with a nominal speed of approx. 3000 rpm, the speed adjustment is between 60 rpm and 180 rpm. The speeds of the two centrifugal pumps then differ by a maximum of between 60 rpm and 180 rpm. Alternatively, the maximum speed difference can also be specified in absolute speed values. This way, the Adjustment of the speed, for example, can be a maximum of 40 rpm to 60 rpm.
  • the adjustment of the speed of at least one of the centrifugal pumps mentioned is to be understood here as referring to the original speed setpoint, i.e. to the synchronous speed that is specified for the centrifugal pumps by the speed controller.
  • the speed can be changed in discrete steps or continuously. Discrete steps have the advantage that the process can be carried out iteratively and after each step it can be checked whether the speed change achieves the desired goal. The performance comparison and the adjustment of the speed can thus be repeated after each speed change depending on the result of this performance comparison.
  • the step size can be between 1 rpm and 10 rpm, for example. This comparatively small step size ensures that the process slowly moves towards symmetrical power consumption and does not influence the higher-level speed control, in particular does not impair its stability.
  • the step size can be fixed so that the same step size is used in every operating state.
  • the step size can be variable, depending in particular on the level of the difference in the power consumed. This has the advantage that the respective operating state of the pump system can be taken into account.
  • the step size can be higher the higher the power difference. For example, for a power difference of up to 2W, a step size of 1 rpm can be used, for power differences of 2W to 5W, a step size of 2 rpm, and for power differences between 5W and 10W, a step size of 5 rpm. This means that power symmetrization is achieved more quickly.
  • the described method is repeated again and again in order to be able to determine dynamically during operation whether a speed change is required, in which direction this should be carried out and whether a previous speed change had the right effect. It is particularly advantageous if the performance comparison and the adjustment of the speed depending on the result of this performance comparison are only repeated after a waiting time has elapsed.
  • This waiting time can be between 0.1s and 20s, for example.
  • the waiting time means that the method according to the invention is carried out at low frequencies so that it does not affect the higher-level speed control.
  • FIG 1 shows a pump system 1 with two hydraulically parallel operated centrifugal pumps 2, 3, each driven by a drive unit 7, 8 (not shown) (see Figure 5 ).
  • These drive units 7, 8 are speed-controlled electric motor drives, which are structurally identical. They are also driven to rotate in the same direction.
  • the two centrifugal pumps 2, 3 are housed in a common pump housing 4. This means that the respective impellers of the centrifugal pumps 2, 3, which are also structurally identical, are each located in a pump housing, but these two pump housings are formed as one piece. This results in the outlet channels of the two centrifugal pumps 2, 3 being arranged and shaped differently in order to be able to pump into a common pressure line 6 with the same direction of rotation of the drive units 7, 8.
  • the pump system according to Figure 1 is commonly referred to as a double pump or twin pump.
  • valve 9 in the common pump housing 4, which has two valve flaps 5a, 5b. Each of these valve flaps can close an outlet of one of the two centrifugal pumps 2, 3.
  • the valve 9 prevents one of the centrifugal pumps 2, 3 from pumping into the outlet channel or pump chamber of the other centrifugal pump when this other centrifugal pump is switched off and only one centrifugal pump is operated. This would cause a hydraulic short circuit.
  • the two valve flaps 5a, 5b are held in a middle position in which they lie back to back. The flow of the respective centrifugal pump 2, 3 is then pumped past the respective valve flap 5a, 5b, whereby the same effective flow cross-section exists.
  • FIG. 2 shows an alternative variant of a double pump 1 in cross section, which is essentially identical in construction to the first variant. Only the design of the pump housings of the respective centrifugal pumps 2, 3 and the design of the valve 9 differ from that in Figure 1 .
  • the valve 9 is formed by a single pivoting flap 5. This flap 5 has two end stops, whereby it closes the outlet of one centrifugal pump 2 when it assumes the first end stop, and closes the outlet of the other centrifugal pump 3 when it assumes the second end stop. The position of the valve flap 5 depends on the discharge pressure of both centrifugal pumps 2, 3.
  • the double pump 1 according to Figure 2 shows the same problem of asymmetry in the flow rates and an electrical power asymmetry as the double pump according to Figure 1 , although the drive units and impellers are identical and operation occurs at synchronous speed.
  • Figure 3 represents the course of the electrical power consumption P1, P2 of the two centrifugal pumps 2, 3 after Figure 1 or their drive units 7, 8 in speed-synchronous operation at 3400 rpm each over the total flow rate Q of the double pump 1.
  • the total flow rate Q was measured here.
  • the linear increase in power consumption P1 of the first centrifugal pump 2 ends when a maximum power consumption is reached, which here is approximately 1.24 kW. Only in this operating state does the valve flap 5b open increasingly, which can be seen from the now present linear increase in electrical power consumption P2 of the second centrifugal pump 3. However, the power consumption P2 of the second centrifugal pump 3 does not initially rise to the value of the first centrifugal pump. Rather, there is a drop in power, after which the power consumption P2 continues to rise again as the flow rate Q increases.
  • the valve 9 assumes a position in which the total volume flow Q is not formed symmetrically, i.e. not half each, by the partial volume flows of the two centrifugal pumps 2, 3.
  • the first centrifugal pump 2 contributes more to the total flow rate Q of the double pump 1 than the second centrifugal pump 3. If the two centrifugal pumps 2, 3 have the same speed n_soll, this means that the second centrifugal pump 3 also works against a partially closed valve flap 5b in the medium volume flow range, which causes hydraulic losses.
  • FIG. 5 A block diagram of the inventive control of the pump system 1 is shown in Figure 5 shown.
  • the block diagram schematically shows the two hydraulically parallel operated centrifugal pumps 2, 3, which pump into the common pressure line 6 via the valve 9.
  • the electromotor drive units 7, 8 of the two centrifugal pumps 2, 3 are also shown, each of which is fed by its own frequency converter 14, 15.
  • the frequency converters 14, 15 comprise a power electronic part (hardware) and a control part (software) that controls the power electronic part.
  • the frequency converters 14, 15 apply a voltage U of a specific frequency f to the drive units 7, 8 (electric motors M1 and M2). This voltage U and frequency f depend on a speed setpoint specification n_soll1, n_soll2 that each of the two frequency converters 14, 15 receives.
  • the electrical power P1, P2 consumed by the respective drive unit 7, 8 is recorded by suitable means 16, 17, for example by measuring using appropriate sensors. The determined actual values of the power consumption P1, P2 are made available to the control system.
  • the actual speeds n_ist1, n_ist2 of the two centrifugal pumps 2, 3 are determined from electrical converter variables. In principle, this determination can also be carried out by measuring the respective drive unit 7, 8. However, this requires sensors, which lead to additional costs and assembly effort. It is therefore advantageous to determine the actual speeds without sensors. This can be done in a known manner based on an electrical and electromechanical model of the frequency converter and drive motor, which also takes the centrifugal pump into account in particular, whereby such a model is already implemented in the control units (software) of the frequency converters 14, 15 for their control.
  • the control consists of a conventional speed control using a hydraulic controller 10, which outputs a synchronous speed n_soll for both centrifugal pumps 2, 3.
  • the hydraulic controller 10 can control in a known manner according to a predeterminable characteristic curve control, for example a ⁇ p-constant or ⁇ p-variable control. However, other types of control can also be used.
  • the type of control can be specified for the hydraulic controller 10. Other external specifications can also be made that influence the speed control, for example the specification of a minimum and a maximum speed.
  • the power consumption P1, P2 and the determined actual speeds n_ist1, n_ist2 are fed to the hydraulic controller 10.
  • the synchronous speed n_soll output by the hydraulic controller 10 is fed to a power balancing 12 downstream of this control system, which represents the core of the control according to the invention.
  • the power balancing 12 adjusts the synchronous speed n_soll individually for the respective centrifugal pump 2, 3 with the aim of achieving the same power consumption P1, P2. To do this, it determines a target speed n_soll1 for one centrifugal pump 2 and a target speed n_soll2 for the other centrifugal pump 3 depending on the result of a power comparison of the current power consumptions P1, P2.
  • These individual target speeds n_soll1, n_soll2 are then fed to the converters 14, 15, or more precisely to their control units, which then control the respective frequency converter 14, 15 accordingly.
  • the inverter control units, the hydraulic controller 10 and the power balancing 12 can each be implemented in their own hardware or in shared hardware, for example comprising their own or shared microprocessor, ASIC (application-specific integrated circuit) or DSP (digital signal processor) and their own or shared memory (ROM, RAM, EEPROM).
  • ASIC application-specific integrated circuit
  • DSP digital signal processor
  • ROM read-only memory
  • RAM random access memory
  • EEPROM electrically erasable programmable read-only memory
  • the shared use of these components means that the software implementing the speed control 10, the power balancing 12 and the inverter control units each comprises their own processes, but which run on the same hardware using the same resources.
  • Figure 6 shows an example of the process according to the invention. It illustrates an example of the power symmetry in a flow chart.
  • the two centrifugal pumps 2, 3 are always adjusted in opposite directions in their speed n_soll1, n_soll2.
  • a hysteresis is taken into account in this example and the process is repeated again and again at intervals of 3 seconds. This waiting time is implemented by querying a timer.
  • Initialization can be performed when the pump system is commissioned and/or during operation, for example by performing a reset, i.e. resetting the pump settings to the factory settings.
  • the initialization 20 includes setting a variable n_offset to zero.
  • This variable describes the distance, ie the difference between the individual centrifugal pump speeds n_soll1, n_soll2 and the synchronous target speed n_soll, which is specified by the hydraulic controller 10.
  • a parameter value P_hyst is defined that describes the hysteresis. This is given here as an example as 2% of the maximum power. It can also be different, for example between 1% and 5%. Furthermore, it can alternatively be defined as an absolute value or as a relative value based on a reference value other than the maximum power.
  • step 20 the initialization of further parameters and variables can take place, for example a parameter n_limit, which defines a maximum adjustment of the target speed n_soll and/or absolute speed limit values n_min, n_max for the centrifugal pumps 2, 3.
  • n_limit defines a maximum adjustment of the target speed n_soll and/or absolute speed limit values n_min, n_max for the centrifugal pumps 2, 3.
  • the hydraulic controller 10 first determines the target speed n_soll according to external specifications and the set control type, with which both centrifugal pumps 2, 3 of the double pump 1 should be operated in order to reach a certain operating point of the double pump 1.
  • the determination of the speed target value n_soll from the hydraulic controller 10 is carried out in step 22 in Figure 6 shown.
  • this target speed n_soll is not fed directly to the converters 14, 15 of the two centrifugal pumps 2, 3.
  • this synchronous target speed n_soll is individualized for the individual centrifugal pumps 2, 3 in such a way that their power consumption, P1, P2, becomes approximately the same, provided that certain conditions are met.
  • the core of the method according to the invention begins with checking whether the timer has expired, step 24.
  • the timer ensures that the method is repeated at intervals.
  • the interval can be set and, as previously mentioned, can be 3 seconds, for example.
  • the timer expiration check in the example according to Figure 6 is carried out at the beginning of the power balancing, the timer expiration can also take place at another point, for example before or after step 30.
  • the first power unit comparison takes place in step 26.
  • step 26 it is checked whether the power consumption P1 of the first centrifugal pump 2 is greater than the power consumption P2 of the second centrifugal pump 3 plus the hysteresis P_hyst.
  • step 26 the further condition is checked whether the speed adjustment n_offset has (already) reached a specified maximum value n_grenz. This is because only if this limit value n_grenz has not yet been reached should an adjustment or further adjustment of the synchronous speed setpoint n_soll take place.
  • the synchronous speed n_soll is adjusted in order to symmetrize the power consumption P1, P2 of the two centrifugal pumps 2, 3.
  • This adjustment takes place in the form of a speed offset n_offset related to the synchronous speed n_soll.
  • the power consumption P1 of the first centrifugal pump 2 is greater than the power consumption P2 of the second centrifugal pump 3, in particular is higher by at least the amount of the hysteresis value P_hyst, the synchronous speed n_soll is adjusted.
  • step size x can be fixed, for example between 1 rpm and 10 rpm. However, it is also possible to make the step size x dependent on the size of the difference between the power consumption P1, P2 of the two centrifugal pumps 2, 3, whereby the higher this difference is, the higher the step size is. For the sake of simplicity, a fixed value of 1 rpm is used here as an example.
  • step 30 the speed offset n_offset is added to the synchronous speed setpoint n_soll to obtain the speed setpoint n_soll1 of the first centrifugal pump 2 and is subtracted from the synchronous speed setpoint n_soll to obtain the speed setpoint n_soll2 of the second centrifugal pump 3. Since the speed offset n_offset is negative at this exemplary point in the method, i.e.
  • step 30 ie when a new current speed setpoint n_setpoint is specified by the hydraulic controller 10, which may be changed compared to the previous synchronous speed setpoint n_soll.
  • step 24 It is then checked again whether the timer has expired, step 24. If this is not the case, the previously calculated speed offset n_offset is subtracted again in step 30 from the synchronous speed setpoint n_soll newly specified by the hydraulic controller 10 in order to obtain the speed setpoint n_soll2 for the second centrifugal pump 3, or added to obtain the speed setpoint n_soll1 for the first centrifugal pump 2.
  • the first partial comparison for power symmetrization is carried out again. If the power consumption P1 of the first centrifugal pump 2 is still greater than the power consumption P2 of the second centrifugal pump 3 plus the hysteresis value P_hyst, the speed offset n_offset is reduced by a further step of step size x, provided that the check of the second condition resulted in the result that the maximum speed offset n_limit has not yet been reached, i.e. the speed offset has not yet been reduced so much that it is smaller than the maximum speed offset n_limit with a negative sign.
  • step 30 in which the further reduced speed offset n_offset for the second centrifugal pump 3 is subtracted from the current synchronous target speed n_soll and added for the first centrifugal pump 2.
  • the process according to this loop is repeated as long and as often as the power consumption P1 of the first centrifugal pump 2 is higher than the power consumption P2 of the second centrifugal pump 3 plus the hysteresis value P_hyst and the speed offset n_offset has not yet reached the defined maximum value n_grenz.
  • This maximum value n_grenz can be, for example, between 40 and 80 rpm, in particular 60 rpm.
  • step 28 the second power section comparison is carried out in step 28. In this, it is checked whether the power consumption P1 of the first centrifugal pump 2 is less than the power consumption P2 of the second centrifugal pump 3 minus the hysteresis value P_hyst. If this condition and the further condition are met, according to which the speed offset n_offset has not yet reached its maximum value n_grenz, this time with a positive sign, then in step 29 the speed offset n_offset is increased by one step of the step size x. This step size x can also be between 1 rpm and 10 rpm. 1 rpm is used here as an example.
  • step size x by which the speed offset is reduced in step 27 does not necessarily have to be identical in height to the step size x by which the speed offset n_offset is increased in step 29. Rather, different step sizes can also be selected for changing the speed offset n_offset.
  • the speed offset n_offset increased by the amount x is then added back to the synchronous speed setpoint n_soll in step 30 to obtain the speed setpoint n_soll1 for the first centrifugal pump 2, and subtracted from the synchronous speed setpoint n_soll to obtain the speed setpoint n_soll2 of the second centrifugal pump 3.
  • the electrical power consumption P1 of the first centrifugal pump 2 is smaller than the electrical power consumption P2 of the second centrifugal pump 3, taking into account the hysteresis P_hyst as determined in step 28, the speed n_soll1 of the first centrifugal pump 2 is increased and the speed n_soll2 of the second centrifugal pump 3 is reduced by increasing the speed offset n_offset in step 29 in step 30, in order to bring the two power consumptions P1, P2 closer together.
  • step 24 If the time period of three seconds has expired again, step 24, and the power consumption P2 of the second centrifugal pump 3 is still higher than the power consumption P1 of the first centrifugal pump 2 plus the hysteresis value P_hyst, the speed offset n_offset is increased again by one step of the amount x, step 29, provided that the maximum speed offset n_grenz has not yet been reached. If this is not the case, the target speed n_soll1 of the first centrifugal pump 2 is increased further and the target speed n_soll2 of the second centrifugal pump 3 is reduced further in step 30.
  • the maximum speed offset n_limit in step 26 does not necessarily have to be identical in amount to the maximum speed offset n_limit in step 28. Rather, different maximum speed offsets can also be used in the aforementioned steps 26, 28.
  • FIG. 7 shows a representation of the power consumption P1(Q), P2(Q) of the first and second centrifugal pumps 2, 3, each over the total flow rate Q delivered by the double pump 1.
  • P1, P2 at least compared to the curve in Figure 3 a clear convergence of the performance curves to each other, especially on average, can be seen.
  • the power consumption P1, P2 of both centrifugal pumps 2, 3 gradually increases on average, with the power consumption P1 of the first centrifugal pump 2 increasing significantly more slowly than is the case in the absence of the power symmetrization 12 according to the invention.
  • the second Centrifugal pump 3 no longer works against a closed or at least partially closed valve flap 5b, 5, so that fewer hydraulic losses occur and the efficiency of the double pump 1 is improved.
  • the fluctuations in the power consumption P1, P2 can be improved by reducing the timer waiting time, but cannot be completely compensated.
  • the waiting time implemented with the timer should not be too short in order not to influence the superimposed fast speed control.
  • Figure 8 shows analogous to Figure 4 the target speeds n_soll1, n_soll2 for the two centrifugal pumps 2, 3, which are individually adjusted depending on the result of the two power unit comparisons. It is clear that the target speeds n_soll1, n_soll2 are always offset from each other by a speed offset n_offset. Due to the symmetrical offset n_offset selected here in relation to the synchronous speed n_soll, this would be shown in the diagram of the Figure 8 run in the middle between the two speed curves for n_soll1(Q) and n_soll2(Q).
  • the speed offset n_offset is significantly smaller in the range of small flow rates Q, here for example in the range of less than 20m 3 /h, than in the range of medium and high flow rates Q.
  • the speed offset n_offset increases with increasing flow rate Q, although it decreases again at high flow rates Q in the direction of the maximum flow rate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)

Claims (13)

  1. Procédé de régulation d'une pompe double (1) présentant deux pompes centrifuges (2, 3) à fonctionnement hydraulique parallèle, disposées dans un corps de pompe commun (4) et chacune étant entraînée par son unité d'entraînement à moteur électrique et vitesse variable (7, 8), caractérisé en ce que la vitesse variable des pompes centrifuges (2, 3) est régulée par une commande à courbes caractéristiques (10), définissant une valeur nominale de vitesse de rotation (n_soll) synchrone pour toutes les pompes centrifuges (2, 3), sachant que la puissance électrique absorbée déterminée (P1) d'une des pompes centrifuges (2) est comparée à la puissance électrique absorbée déterminée (P2) de l'autre pompe centrifuge (3) et que, en fonction du résultat de cette comparaison, la valeur nominale de vitesse de rotation (n_soll1, n_soll2) d'au moins une des pompes centrifuges (2, 3) est adaptée en aval de la commande à courbes caractéristiques de telle façon que les puissances absorbées (P1, P2) des pompes centrifuges (2, 3) présentent un rapport prédéterminé et, tout particulièrement, soient harmonisées.
  2. Procédé selon la revendication 1, caractérisé en ce que les pompes centrifuges (2, 3) sont montées sur une conduite de pression (6) commune, à laquelle elles sont reliées par une vanne non commandée (9) présentant au moins un moyen de réglage (5, 5a, 5b), la position du moyen de réglage (5, 5a, 5b) dépendant de la pression ou du flux de transport des deux pompes centrifuges (2, 3).
  3. Procédé selon l'une des revendications précédentes, caractérisé en ce que l'adaptation de la vitesse de rotation (n_soll) ne se fait que lorsque la différence de puissance entre les unités d'entraînement (7, 8) dépasse une valeur limite prédéterminée (P_hyst).
  4. Procédé selon l'une des revendications précédentes, caractérisé en ce que la vitesse de rotation (n_soll1) de la première pompe centrifuge (2) est réduite par rapport à la vitesse de rotation (n_soll2) de l'autre pompe centrifuge (3) et/ou la vitesse de rotation (n_soll2) de l'autre pompe centrifuge (3) est augmentée par rapport à la vitesse de rotation (n_soll2) de la première pompe centrifuge (2), lorsque la puissance absorbée (P1) de la première pompe centrifuge (2) est plus haute, en particulier à hauteur d'une première valeur limite (P_hyst), que la puissance absorbée (P2) de l'autre pompe centrifuge (3).
  5. Procédé selon l'une des revendications précédentes, caractérisé en ce que la vitesse de rotation (n_soll1) de la première pompe centrifuge (2) est augmentée par rapport à la vitesse de rotation (n_soll2) de l'autre pompe centrifuge (3) et/ou la vitesse de rotation (n_soll2) de l'autre pompe centrifuge (3) est réduite par rapport à la vitesse de rotation (n_soll2) de la première pompe centrifuge (2), lorsque la puissance absorbée (P1) de la première pompe centrifuge (2) est plus basse, en particulier à hauteur d'une seconde valeur limite (P_hyst), que la puissance absorbée (P2) de l'autre pompe centrifuge (3).
  6. Procédé selon l'une des revendications précédentes, caractérisé en ce que l'adaptation de la vitesse de rotation (n_soll) représente au plus ±2% à ±6% de la vitesse de rotation nominale des pompes centrifuges (2, 3), en particulier de 50 tr/min à 60 tr/min maximum.
  7. Procédé selon l'une des revendications précédentes, caractérisé en ce que l'adaptation de la vitesse de rotation (n_soll) se fait pas à pas.
  8. Procédé selon la revendication 7, caractérisé en ce que l'amplitude des pas est entre 1 tr/min et 10 tr/min.
  9. Procédé selon la revendication 7, caractérisé en ce que l'amplitude des pas dépend de la valeur de la différence des puissances enregistrées (P1, P2).
  10. Procédé selon la revendication 9, caractérisé en ce que l'amplitude des pas est proportionnelle à la différence de puissance.
  11. Procédé selon l'une des revendications précédentes, caractérisé en ce que la comparaison des puissances est répété de façon récurrent après l'écoulement d'un délai.
  12. Pompe double (1) présentant deux pompes centrifuges (2, 3) à fonctionnement hydraulique parallèle, disposées dans un corps de pompe commun (4) et chacune pouvant être entraînée par son unité d'entraînement à moteur électrique et vitesse variable (7, 8),
    caractérisé par
    - un dispositif (16) de détermination de la puissance électrique absorbée (P1) d'une des pompes centrifuges (2),
    - un dispositif (17) de détermination de la puissance électrique absorbée (P2) de l'autre pompe centrifuge (3),
    - une unité de contrôle configurée pour comparer les puissances absorbées (P1, P2),
    - une commande à courbes caractéristiques (10) destinée à la régulation des vitesses des pompes centrifuges (2, 3) et configurée pour définir une valeur nominale de vitesse de rotation (n_soll) pour toutes les pompes centrifuges (2, 3), et
    - une commande de pompe (12) en aval de la commande à courbes caractéristiques (10), configurée pour, en fonction du résultat de la comparaison des puissances absorbées, adapter la valeur nominale de vitesse de rotation (n_soll1, n_soll2) d'au moins une des pompes centrifuges (2, 3) de telle façon que les puissances électriques absorbées (P1, P2) présentent un rapport prédéterminé et, tout particulièrement, soient harmonisées.
  13. Pompe double (1) selon les revendications 12 caractérisé en ce qu'elle est configuré pour l'exécution du procédé selon l'une des revendications 2 à 11.
EP15000541.1A 2014-04-30 2015-02-25 Procédé de réglage d'un système de pompe et système de pompe réglé Active EP2940309B2 (fr)

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DE102014006258.9A DE102014006258A1 (de) 2014-04-30 2014-04-30 Verfahren zur Regelung eines Pumpensystems und geregeltes Pumpensystem

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Publication number Priority date Publication date Assignee Title
DE102015016086A1 (de) 2015-12-10 2017-06-29 Wilo Se Doppelpumpe
DE102017203926A1 (de) * 2017-03-09 2018-09-13 KSB SE & Co. KGaA Verfahren zum Betrieb einer Umwälzpumpe in Zwillingsbauweise
EP3428453B1 (fr) * 2017-07-14 2023-06-07 Grundfos Holding A/S Commande multi-pompe gardant le rapport de pression constant pendant la mise en marche ou l'arrêt d'une partie des pompes
DE102017223189A1 (de) * 2017-12-19 2019-06-19 KSB SE & Co. KGaA Mehrpumpenanlage und Verfahren zu deren Betrieb
RU2711889C1 (ru) * 2019-02-15 2020-01-23 Публичное акционерное общество "Ракетно-космическая корпорация "Энергия" имени С.П. Королёва" Дублированный электронасосный агрегат
LU102816B1 (de) 2021-06-01 2022-12-01 Wilo Se Doppelpumpenaggregat
JP2022187176A (ja) * 2021-06-07 2022-12-19 株式会社荏原製作所 ポンプケーシング
CN114109858B (zh) * 2021-09-24 2023-12-01 中国船舶重工集团公司第七一九研究所 一种锅炉给水泵集群转速均衡控制方法和系统
LU503228B1 (de) 2022-12-21 2024-06-21 Wilo Se Doppelpumpe mit Isolierverkleidung und zugehöriges Montageverfahren

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DE1653743B2 (de) * 1967-08-12 1976-01-29 Loewe Pumpenfabrik GmbH, 3140 Lüneburg Warmwasser - heizungsanlage mit einer einen antrieb aufweisenden umwaelzeinrichtung
DE3918246A1 (de) 1989-06-05 1990-12-06 Eggs Elektrotechnik Druckerhoehungseinrichtung
DE4330507C1 (de) * 1993-09-09 1994-10-06 Grundfos As Klappenumschaltvorrichtung für die Druckseite einer Doppelpumpe
DE19511170A1 (de) 1995-03-28 1996-10-02 Wilo Gmbh Doppelpumpe mit übergeordneter Steuerung
EP1614903B1 (fr) 2004-07-07 2019-05-22 Grundfos A/S Unité moteur pour entrainer une pompe centrifuge
PL2229610T3 (pl) 2007-12-14 2019-08-30 Itt Manufacturing Enterprises Llc Równowaga synchronicznego momentu obrotowego w układach wielopompowych
US8180496B2 (en) 2008-03-05 2012-05-15 Metropolitan Industries, Inc. System and method of constant pressure, variable speed pump control with local equalization for dissimilar pumps
EP2161455B1 (fr) * 2008-09-04 2018-05-30 Grundfos Management A/S Pompe double
DE102010055841A1 (de) 2010-12-23 2012-06-28 Wilo Se Verfahren zum Betrieb eines Doppelpumpen- oder Multipumpenaggregates
CA2831759C (fr) 2013-10-31 2015-01-20 Westport Power Inc. Appareil et procede pour faire fonctionner une pluralite de pompes hydrauliques

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EP2940309B1 (fr) 2019-10-23
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