Management and control methods of boosting system

Abstract

The invention relates to a method for managing and controlling at least one operating parameter of a supercharging system operated by an electric motor, the method comprising the steps of: - detecting the operating pressure value at the delivery pipeline of the supercharging system by means of a single pressure sensor; - estimating the hydraulic flow and the hydraulic head by means of an algorithm implemented in the control software based on the operating pressure value detected by means of a single pressure sensor (10); - estimating the motor speed of the supercharging system based on the operating pressure value and the number of blades of the impeller of the supercharging system according to the estimated result; - processing the on / off signal of the supercharging system. The invention also relates to a supercharging system comprising a pressure value and an electronic control unit suitable for executing the method. The method according to the invention allows to optimize energy consumption while maintaining maximum comfort for use of public facilities.

Description

Technical Field

[0001] The invention relates to a method for managing and controlling at least one operating parameter of a supercharging system operated by an electric machine.

[0002] The method described above is particularly, but not exclusively, applicable in the field of pumps and pressure boosting units equipped with fixed or variable speed electric motors, in particular electric motors of the asynchronous type. Background Art

[0003] It is known in the art that in a stable water supply network, if the network pressure is insufficient or insufficient to stably supply water to users at high water levels, a pressurizing device, usually called a "boosting pump", is used. Usually, at least one main boosting system and at least one auxiliary boosting system are provided.

[0004] These booster units are typically designed so that the required pressure level at the delivery of the booster unit can be maintained within a certain range of values. The pump is therefore dimensioned to maintain the system pressure between upper and lower limit values ​​with a defined inlet pressure. To this end, the booster pump is always switched on when the pressure level on the outlet side of the booster unit drops below a lower limit value and is switched off again when the upper limit value is reached. If the inlet pressure of the auxiliary pump drops to a value that does not allow this lower limit value to be reached, the booster unit will continue to operate without restriction at maximum pump power, resulting in correspondingly high energy consumption, pump wear and heating of the conveyed medium, while at the same time not achieving the desired pressure level effect. In particular, in continuous start-stop operation, especially in pumps operated with asynchronous motors, the component most susceptible to damage is the condenser.

[0005] To overcome this disadvantage, a water tank (also called an expansion tank) is usually used in the hydraulic circuit to minimize the number of times the conventional booster system is opened and closed. The usual practice is to control it within 30 openings / closings per hour. However, this expedient is often not enough.

[0006] Therefore, methods and systems for measuring the flow rate have now been developed in order to determine the correct operating pressure value and to establish the best conditions of use for the utility. This estimation is particularly necessary for pumps operated by asynchronous motors.

[0007] Patent application document WO 2014 / 023642 A1 describes a mathematical method for estimating the flow rate of a boosting system (particularly a centrifugal pump), which uses the pump speed value, the pump hydraulic variable (usually the delivery pressure), and one of the electrical variables of the motor drive, such as electrical power.

[0008] Patent application document WO 2005 / 085772 A1 describes a method for measuring the flow rate of a boosting system operated by an AC motor, wherein the speed of the AC motor is controlled by a frequency converter. The flow rate is determined by using characteristic data of the boosting system and measured parameters (such as the motor speed, fluid pressure and motor power of the boosting system).

[0009] Patent document GB2313197B describes a method for estimating the flow rate of a boosting system, which compares the test data provided by the manufacturer of the boosting system (in this case, the power, capacity and hydraulic head absorbed by the pump of the boosting unit) with the same quantitative data measured under operating conditions. Two pressure transducers are used to determine the hydraulic head H under operating conditions, the first hydraulic head for suction and the second hydraulic head for delivery of the boosting system.

[0010] Although currently known methods are advantageous and may be an alternative to the use of expensive flow sensors, they provide for the use of multiple measurement tools, resulting in greater overall system complexity and cost.

[0011] Furthermore, employing multiple measurement systems may result in different potential measurement errors that may be combined and amplified in the overall estimate of flow.

[0012] For this reason, an object of the present invention is to conceive a method for management and control of a booster system which allows obtaining reliable flow values ​​while minimizing the parameters required for the estimation.

[0013] Another object is to provide a method capable of monitoring the operating status of a boosting system to optimize the operation of each step of the boosting system over a period of time.

[0014] Another object is to provide a method that allows to obtain an optimization of energy consumption while maintaining maximum comfort for the use of the public facility.

[0015] Finally, another object is to provide a method that minimizes the structural requirements of the system in order to control costs. Summary of the invention

[0016] The solution concept of the invention is to provide a method which allows the operating state of a supercharging system to be determined and optimized by estimation starting from a minimum number of measured data.

[0017] The above technical problem is solved by a method for managing or controlling at least one operating parameter of a supercharging system or a pump operated by an electric motor, the method comprising a step of detecting an operating pressure value at a delivery pipe of the supercharging system by means of a single pressure sensor. The method also comprises a step of estimating the hydraulic flow and the hydraulic head by means of an algorithm implemented in a control software, wherein the control software is based on the operating pressure value detected by the single pressure sensor. The method also comprises a step of estimating the motor speed of the supercharging system based on the operating pressure value and the number of blades of a propeller of the supercharging system. Finally, the method comprises a step of processing an on / off signal of the supercharging system according to the estimation.

[0018] Advantageously, the invention allows estimating the hydraulic flow, the motor speed of the booster system and the required expansion tank performance through a single integrated physical pressure sensor in the delivery pipe of the booster unit and an algorithm implemented in the control software. It is thus possible to adjust the minimum and maximum pressure thresholds for the operation of the booster system and monitor the usage when the utilities connected to the hydraulic circuit of the booster system are turned off / on. In this way, it is possible to ensure maximum comfort for the user.

[0019] Preferably, the method of the invention comprises a preliminary step of storing nominal operating parameters of the pressure boosting system in a part of a memory of an electronic control unit of the pressure boosting system or of the pump.

[0020] Advantageously, the pressure boosting system is therefore provided with a series of test data which are acquired and stored in a testing step in the production line, which data are specific to each model of pump and / or pressure boosting unit produced.

[0021] Preferably, the signal processing step comprises the step of updating the value of the nominal hydraulic head of the nominal operating parameter of the booster system, starting from the above-mentioned operating pressure value and from the said motor speed in the operating conditions, once installed in the booster system. In this way, the updated data can be applied based on the specific functions required in the installation.

[0022] Also preferably, the signal processing step comprises the step of calculating optimal values ​​of the input and suction hydraulic heads of the boosting system within a range of reference values.

[0023] In this way, advantageously, the user can be provided with an optimal supply under any conditions and at any time during use.

[0024] Preferably, the signal processing step comprises the steps of calculating the pressure variation between the input hydraulic head and the nominal hydraulic head and optimizing the opening time of the boost system according to the on / off signal.

[0025] Advantageously, this allows for correct opening timing of the booster system, thereby reducing energy consumption and increasing reliability of pump components that are subject to wear and tear due to unnecessary opening and closing to properly supply the booster system with water.

[0026] According to a preferred embodiment, the step of calculating the optimal value of the input hydraulic head of the boosting system is implemented by the following steps: setting initial pressure parameters of the boosting system, calibrating the boosting system by an iterative process of comparison between the weighted difference in the running hydraulic head and a preset reference value, and identifying the reference value and the minimum energy consumption situation of the input and suction hydraulic heads in a preset time period.

[0027] Advantageously, the present procedure is the fastest and is simultaneously effective in achieving optimal conditions for the facility from both an operational and energy consumption perspective.

[0028] Preferably, iterative repetitions are provided in order to optimize the energy of the changes in the operation of the supercharging system and to detect operating conditions outside the design of the supercharging system.

[0029] Advantageously, this allows to achieve conditions of maximum efficiency at different moments in time. Furthermore, this allows to identify conditions close to the faucet closing by indirectly evaluating the flow rate, as well as to identify permissible small drops. In fact, these drops imply a change in the slope of the flow operating curve, which however must not correspond to the response of the booster system. This allows to further reduce the number of unnecessary openings and closings of the booster system.

[0030] Preferably, the method provides for applying preset comfort parameters to the nominal hydraulic head and to the values ​​of the inlet and suction hydraulic heads.

[0031] Advantageously, this allows correction values ​​to further improve supply to the facility.

[0032] According to a particular embodiment, the management and control method of the invention comprises a start-up control step of the booster system.

[0033] Advantageously, this additional step allows a preventive check to confirm correct operation or to determine the need for maintenance intervention under self-diagnosis conditions. In this way, the intervention time for maintenance is optimized and even more serious damage can be prevented.

[0034] Preferably, the management and control method comprises the step of estimating the volume of the expansion tank according to the operating conditions of the boosting system, wherein the operating conditions of the boosting system are suitable for maintaining a preset minimum operating threshold for opening and closing the boosting system.

[0035] Advantageously, this also allows optimizing the interface to the water distribution system by advising the plumber on the minimum size of the external expansion tank to be integrated into the system.

[0036] According to another aspect of the invention, a pressure boosting system is provided, the system comprising a single pressure sensor and an electronic control unit adapted to perform a method according to as defined above.

[0037] Advantageously, a booster system constructed in this way allows operation in an optimal configuration with a minimum number of physical components from the standpoint of minimizing consumption and correct and permanent operation of the components, in particular the electrolytic capacitors.

[0038] According to one embodiment, the supercharging system comprises an electric machine of the asynchronous type.

[0039] According to another preferred embodiment, the pressure boosting system comprises an expansion tank.

[0040] Other characteristics and advantages will become more apparent from the following detailed description of a preferred but not the only embodiment of the invention, with reference to the accompanying drawings, given by way of non-limiting example. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] In the attached picture:

[0042] Figure 1 An exemplary boosting system according to the present invention is shown;

[0043] Figure 2 An exemplary flow chart according to the present invention is shown;

[0044] Figure 3 A diagram showing the selection of an expansion water tank for a pressure boosting system according to the present invention;

[0045] Figure 4 A further alternative diagram showing an expansion tank according to the present invention;

[0046] Figure 5 Another exemplary flow chart according to the present invention is shown. DETAILED DESCRIPTION

[0047] With reference to the drawings, reference numeral 1 schematically and as a whole indicates a pressure boosting system made in accordance with the present invention.

[0048] The pressure boosting system 1 comprises an electric motor 2 , a hydraulic unit 3 and an electronic control unit 4 .

[0049] The electric motor 2 and the hydraulic unit 3 are kinematically coupled via a motor shaft.

[0050] The electric motor 2 is preferably a two-phase asynchronous type electric motor.

[0051] The hydraulic unit 3 is accommodated in the volute 5 through the open side 6 of the volute 5 .

[0052] Separated from the volute 5 are a fluid suction conduit 7 and a fluid delivery conduit 8, both of which have internal threads for coupling with supply and distribution conduits (not shown) of a hydraulic system into which the boosting system 1 of the present invention is inserted.

[0053] exist Figure 1 In the exemplary embodiment of the present invention, the electric motor 2 is transversely coupled to the control electronic unit 4. The electronic control unit 4 comprises a control electronic board 9 and an interface display 12. The electronic unit 4 further comprises a pressure sensor 10, which is connected to the electronic control board 9 via a connecting cable 11. The pressure sensor 10 is suitable for detecting the fluid pressure inside the fluid delivery pipeline 8, thereby adjusting the start / stop cycle of the boost system 1.

[0054] In particular, a support element 13 is provided on a side surface of the fluid conveying conduit 8, transverse to the axis of the conveying conduit 8 and adapted to receive the pressure sensor 10. The pressure sensor 10 is removably constrained to the support element 13, for example by threading.

[0055] A sealing element 14, represented in the present embodiment by an O-ring, is inserted between the electronic unit 4 and the pressure sensor 10. Said sealing element 14 performs a retaining and supporting function by correcting any misalignment between the volute 5 and the motor 2.

[0056] A further sealing element 15 is inserted between the support element 13 and the pressure sensor 10 in order to ensure a correct hydraulic seal between the components.

[0057] The electronic unit 4 is suitable for managing and controlling at least one operating parameter of the boosting system 1 .

[0058] During the test step of the boosting system 1 there is an initial step, which is used to store the nominal operating parameters of the boosting system. In particular, the hydraulic and electrical operating parameters of the boosting system 1 are obtained. The pressure Hin of the fluid at the suction pipe 7 of the boosting system 1 is known. The pressure at the delivery pipe 8 is measured by the pressure sensor 10. The power Pn absorbed by the motor and the rotational speed RPMn of the motor 2 are known, the rotational speed of the motor is obtained from the delivery pressure pulses of the boosting system (in particular a centrifugal pump), the number of blades Z of the impeller is known, and appropriate low-pass electronic filtering is performed. The fluid flow Qn is a function of the absorbed power Pn and the rotational speed RPMn. The absolute nominal pressure Hn measured by the pressure sensor 10 can be determined as a function of the liquid flow Qn and the rotational speed RPMn. Knowing Hn and Hin, it is therefore possible to determine the hydraulic head ΔP of the boosting system 1 under test bench conditions (e.g. Hn-Hin).

[0059] These parameters are transferred to the memory of the electronic unit 4 .

[0060] In the actual operation step of the facility, the corresponding hydraulic head value ΔP must be obtained. The value of the absolute nominal pressure Hn must be updated according to the specific application. Therefore, the flow rate Qf under operating conditions and the pressure Hf measured by the pressure sensor 10 at the delivery pipe 8 under operating conditions must be known. Similar to the operation that has been done previously, the speed RPMf under operating conditions can be further obtained from the pressure pulses in the delivery of the boosting system (especially the centrifugal pump) (the number of blades Z of the impeller is known, and appropriate low-pass electronic filtering is performed according to the above parameters and the parameters stored in the electronic unit 4).

[0061] Starting from the operating parameters, in particular the absorbed power Pf, and the parameters stored in the electronic unit 4, the absorbed power can then be calculated under nominal calibration conditions of the supercharging system according to the mechanical similarity of the turbomachine, such as

[0062]

[0063] Similarly, the flow rate under actual operating conditions can be calculated:

[0064]

[0065] Then, starting from the value calculated in the run step, the updated absolute nominal pressure Hn can be calculated for this application case:

[0066]

[0067] Under actual installation conditions of the booster system, for example, when connected to a local water supply network or a booster system on a local water supply network, the suction pressure Hinf is not always constant.

[0068] However, as described above, it is necessary to know the effective value of the pressure Hinf for calculating the hydraulic head ΔPf of the pressure boosting system.

[0069] The present invention provides a calibration procedure for obtaining this pressure Hin.

[0070] First, a stage of setting parameters F1 is performed. The parameters set are the nominal absolute pressure Hmaxnom measured by the pressure sensor 10, the nominal absolute pressure measured by the pressure sensor 10 under operating conditions Hmaxf under conditions of zero flow Q, the nominal absolute pressure Hinnom of suction, the nominal absolute pressure under operating conditions Hinf when pumping under conditions of zero flow Q, the power Pmaxnom absorbed by the motor, and the power Pmaxf absorbed by the motor during operating steps. The hydraulic head ΔPf under operating conditions corresponds to the difference Hmaxnom-Hinnom.

[0071] They are set as initial reference parameters: Hmaxr=Hmaxnom, Pmaxr=Pmaxnom, Hinr=Hinnom.

[0072] The reference value is further set to correct the set reference parameter.

[0073] Therefore, under conditions of zero flow Q, a weighted comparison is performed between the operating parameter with respect to the set reference parameter and the reference value.

[0074] In particular, if If the ratio of is less than or equal to the reference value, Hinfr=Hinnom is set as the reference operating input pressure, and the flow value is not corrected under the operating condition Qf. Thus, the hydraulic head value ΔPf=Hn-Hinfr is obtained.

[0075] On the contrary, if The ratio of the nominal absolute pressure Hmaxf measured by the pressure sensor 10 under the condition of zero flow Q under the operating condition is greater than the reference value, and the detection value of the nominal absolute pressure Hmaxf measured by the pressure sensor 10 under the operating condition under the condition of zero flow Q is set as the new reference parameter Hmaxr, so Hmaxr = Hmaxf, and the reference operating input pressure value Hinfr is corrected to Hmaxr-Hmaxnom. Therefore, the reference values ​​Hmaxr and Hinfr are used as the opening value and closing value of the boosting system 1.

[0076] The maximum power value absorbed is always equal to Pmaxnom and is calculated according to the mechanical similarity formula for turbomachinery, with the new value Hinfr for ΔPf and Qf.

[0077] After the weighted comparison, the calibration step stops.

[0078] As mentioned above, if a booster system 1 is installed to increase the pressure of a public water supply network, Hinfr is variable. This may result in excessive opening and closing of the booster system 1. In addition, pressure fluctuations occur, especially during the most frequently used periods of the public facility, and the booster system cannot guarantee supply to higher altitudes (e.g., the top floor of an apartment) due to intermittent supply due to a drop in system pressure.

[0079] Therefore, the present invention provides an adaptive process downstream of the calibration step.

[0080] Once the parameters Hinfnom and Hmaxnom are set (usually but not limited to being set between 2 bar and 4 bar), and once the above calibration steps have been performed to obtain the reference values ​​Hmaxr and Hinfr, the booster system 1 is operated by the facility under standard use conditions. Thus, the characteristic parameters Hinfr and Hmaxr are recorded for a predetermined period of time.

[0081] In this regard, a so-called “energy saving” mode may be set, so that the electronic unit 4 controls the boosting system 1 to optimize in particular the number of openings and closings of the boosting system 1 within a reference period of time, thereby optimizing energy consumption.

[0082] The average value of Hmaxr and Hinfr is set as the new operating limit until Hmaxf is greater than Hmaxr, at which time the boost system 1 is shut down.

[0083] After closing, the calibration procedure is repeated. If the maximum absorbed power at the closing pressure is found to be different from Pmaxnom, even if the booster system is closed at a pressure below Hmaxr, a change in the suction conditions (especially Hinfr) is associated and the calibration procedure is repeated.

[0084] Differently, a so-called "comfort" mode may be set, so that the electronic unit 4 controls the pressurizing system 1 to minimize pressure fluctuations during the water supply to the installation.

[0085] In this case, once the mean value ΔPmed between the mean values ​​Hmaxr and Hinfr has been determined, it is determined and stored as a nominal value in the memory of the electronic unit 4:

[0086] H infnom =H infr (medio)+v*ΔP med

[0087] H maxnom =H maxr (medio)-ε*ΔP med

[0088] Here, ε is equal to a predetermined constant, preferably between 0.05 and 0.15.

[0089] The method according to the invention also provides a combined algorithm which allows the requirements of minimum opening time and maximum supply stability to be optimized in a coordinated manner, such as Figure 2 In particular, it can increase the minimum opening time of the boosting system in the "comfort" mode, while reducing the frequency of opening / closing the boosting system 1 in a unit time, so as to close the boosting system 1 when it is determined that the demand for the facility stops.

[0090] The algorithm is based on the recognition of sufficiently rapid positive pressure changes that exceed a preset pressure value used as a threshold, thus foreshadowing a shutdown condition of the facility. The algorithm uses the manufacturing data of the booster system 1, in particular the characteristic curve Q / H relating the flow rate of the booster system 1 itself to the hydraulic head.

[0091] Specifically, the present invention provides a signal acquisition step 16, which filters and averages N samples (preferably 1024 samples) in a sampling time Tc (preferably 200 μs) by a moving average algorithm.

[0092] That is, instruct LPF to take accumulator = + press (kT) - vect (n), vect (n) = press (kT), press_avg (kT) = accumulator / N;

[0093] Among them, accumulator is the cumulative value of sampling, press is the pressure, and press_avg is the average pressure.

[0094] Therefore, the signal acquisition step 16 is repeated iteratively, and after N acquisitions, the average pressure value obtained is compared with the average pressure value of the previous cycle.

[0095] That is, p_diff=press_avg(N)-press_avg_mem;

[0096] press_avg_mem=press_avg(N).

[0097] Among them, press_avg(N) is the average pressure value obtained after N acquisitions, and press_avg_mem is the average pressure value of the previous cycle.

[0098] If the difference p_diff exceeds the threshold value THRESHOLD (ie p_diff>THRESHOLD), the counter is incremented (ie counter++) (step 17), otherwise the same counter is reset (ie counter=0) (step 18).

[0099] Once the counter has been incremented, there is a first storage step 19 of the so-called "state 1", the pressure value of which is associated with the acquisition time (P1, t1).

[0100] Step 19 is:

[0101] save p1 = press_avg;

[0102] Save t1=counter.

[0103] Among them, p1 is the pressure value in "state 1", and t1 is the acquisition time in the associated "state 1".

[0104] Once the counter is reset, i.e. the pressure difference p_diff no longer exceeds the threshold THRESHOLD (i.e. p_diff<=THRESHOLD), there is a second storage step 20 of the so-called "state 2" with the pressure value (P2, t2) associated with the acquisition time. The derivative dp_dt between "state 1" and "state 2" is then calculated, and if this derivative dp_dt is greater than a minimum value MIN_DERIVATIVE, the method sends a shutdown signal to the installation (step 21).

[0105] Step 20 is:

[0106] save p2 = press_avg;

[0107] Save t2 = counter;

[0108] dp_dt=(p2-p1) / (t2-t1).

[0109] Among them, p2 is the pressure value in "state 2", and t2 is the associated acquisition time in "state 2".

[0110] The threshold value for the counter increment is obtained from the Q / H characteristic curve of the boost system. A minimum derivative value is also determined in order to skip slow pressure changes.

[0111] For these determinations, consider the case where the pressure of the booster system 1 is zero and the flow rate is 0.5 m 3 / h (corresponds to approximately 8 l / min).

[0112] Therefore, the threshold and the minimum derivative value depend on the comfort parameter ε:

[0113] Threshold THRESHOLD=Δpε

[0114] Derivative value

[0115] The value of ε is preferably about 0.125.

[0116] According to a preferred aspect of the method of the present invention, during the startup of the booster system 1, the above method is also used for the startup control step.

[0117] In particular, during this start-up step, the electronic unit 4 monitors the derivative before the electric motor absorbs power and verifies that it increases in a time interval Δt selected according to the model or pump of the boosting system 1 .

[0118] At the same time, the above algorithm is applied to the detection of the minimum flow rate at the delivery pipeline 8 of the boosting system to verify whether the minimum flow rate Qmin of the normal model or pump of the boosting system 1 is exceeded.

[0119] If the above conditions occur simultaneously within a defined time interval Δt, the booster system will start and follow standard operation. However, if neither condition is verified, the booster system will stop operating and the startup process will be repeated a predetermined number of times n (which is also typical for the model of the booster system 1). If the conditions are not verified after the predetermined number of starts, the booster system 1 enters an alarm state and eventually stops, requiring intervention by an external operator.

[0120] The values ​​of Δt, Qmin and n are implemented in specific reference tables.

[0121] According to a preferred aspect, the method according to the invention can equip the pressure boosting system 1 with a water tank (also called an expansion tank) which is activated when a preset operating threshold is reached.

[0122] The need for a water storage system arises from the need to deliver water at a constant rate in response to utility demand during the day.

[0123] The capacity of the water storage tank must ensure the amount of water required during periods of maximum demand and accommodate the same amount of water when the flow rate required by the utility is lower than the average flow rate provided.

[0124] like Figure 3 Once the flow rate and hourly consumption are defined, they can be plotted against time to determine the minimum capacity of the expansion tank, as shown in the example in .

[0125] Specifically, once the limiting points 0 and P of the integral curve are determined, the connecting point of these points and two parallel lines are drawn, and the following operations are performed for the integral curve point connecting point 0 and point P that are farthest from segment O: The vertical segment intercepted by the two parallel lines represents the minimum volume V of the expansion tank when the flow rate is equal to the average daily consumption, in proportion to the integral curve.

[0126] For example, an autoclave can be used as an expansion tank, about which the cycle time, capacity, especially with regard to the use of a pressurized air compressor for the system, and the maximum insertion frequency can be obtained by known analysis.

[0127] like Figure 4 As shown in the example, the size of the expansion tank can be defined based on the Q / H characteristics of the booster system.

[0128] Therefore, the method according to the invention provides for Figure 4A flow limit is established between the highlighted conditions in the figure to evaluate the loss or supply conditions of the water network downstream of the pressurization system 1, which determines the boundary value between "loss" and "flow useful for delivery to the public facility", which is Q = 6 l / min in the illustrated example. Each line is a function of the pressurization system hysteresis, the maximum number of starts of the pressurization system 1 and the number of cycles per hour, and the type of expansion tank used. Given the flow value and the above fixed limit, the minimum capacity value of the expansion tank can be obtained. Once connected to the pressurization system 1, the estimated value of the flow, the pressure measured by the pressure value 10, and the electrical parameters of the motor 2 can be read on the interface display 12.

[0129] By way of example, Figure 5 A flowchart representing a method for a pressurization system including a water tank according to the present invention is shown.

[0130] Among them, a pressure check is performed after reset (step 22). When the pressure is greater than or equal to the start pressure, that is, press >= pressureStart, the reset process is repeated. When the pressure is less than the start pressure, that is, press < pressure Start, the acceleration process is started (that is, RAMP_UP-START is executed), the acceleration process is executed (that is, RAMP_UP is executed), and the acceleration process is ended (that is, RAMP_UP-END is executed).

[0131] After the pressure control step 22, under the pressure condition lower than the start pressure, the method according to the present invention is started. As Figure 5 shown, after the update step 23 of the counter (Min_Time_Run_Counter++), the second counter is used as a timer to measure the running time of the pressurization system 1 (step 24: minimum running time check Min_Time_Run Check).

[0132] When the minimum running time Min_Time_Run < 3 s, it is determined that fc_defect_enable is false (fc cannot be detected). Then return to the update step of the counter. When the minimum running time Min_Time_Run >= 3 s, mode selection is performed.

[0133] Regarding the running time and the selected mode - "ECO (energy saving) mode" or "COMFORT (comfort) mode" - an algorithm branch is applied.

[0134] In the "ECO (Energy Saving)" mode (step 25), after the verification step 26 that the pressure does not exceed the stop pressure (equal to Hmaxr), the booster system 1 stops after 30 seconds. That is, when the minimum running time Min_Time_Run>=30s, the pressure check is performed, and when the pressure is less than the stop pressure p_Stop, the counter update step (Min_Time_Run_Counter++) is returned; when the pressure is greater than or equal to the stop pressure p_Stop, the deceleration process is started (i.e., RAMP_DOWN-START is executed), the deceleration process is executed (i.e., RAMP_DOWN is executed), and the deceleration process is ended (i.e., RAMP_DOWN-END is executed), thereby ending Figure 5 The process in .

[0135] In the "COMFORT" mode 27, an activation check "fcDetect" is performed when the utilities are switched off (step 28). If activation is proven and an event of a possible closure of the utilities is determined, the booster system 1 is switched off after 5 seconds after a verification step 29 that the pressure has not exceeded the stop pressure (equal to Hmaxr).

[0136] Advantageously, with the method according to the invention, the flow rate for controlling the booster system can be obtained by simply measuring the pressure with a pressure sensor located at the delivery pipe of the booster system and once the electrical variables of the motor (ie the current and the absorbed power) are known.

[0137] Advantageously, the pressure sensor is used to estimate the rotational speed of the impeller of the pressure boosting system starting from the pressure pulsations in a time unit measured by the pressure sensor at the delivery line of the pressure boosting system.

[0138] Advantageously, using a single pressure value, the method according to the invention implemented in the electronic unit of the pressurization system allows detecting a positive variation in pressure corresponding to a possible partial or total closure of the utility.

[0139] Furthermore, the method according to the invention allows optimizing energy consumption while maintaining maximum user comfort of the public facility.

[0140] Those skilled in the art will also understand how to minimize the structural requirements of the system, and therefore minimize cost, to ensure the same confidence in the data as would be obtained using a more complex system.

[0141] It will be understood by those skilled in the art that various modifications and changes may be made to the embodiments herein according to possibility and specific needs, all of which are included in the protection scope of the present invention as defined in the claims.

Claims

1. A method for managing and controlling at least one operating parameter of a booster system (1) operated by an electric motor (2), the system comprising a pump having an impeller, It is characterized in that The method comprises a preliminary step of storing nominal operating parameters of the pressure boosting system (1) in a memory section of a control electronics unit (4) of the pressure boosting system (1) under test bench conditions, the nominal operating parameters comprising a nominal absolute pressure (Hmaxnom) and a nominal absolute suction pressure (Hinnom), and the method further comprises the following steps under operating conditions: - detecting the operating pressure value at the delivery pipeline (8) of the boosting system (1) by means of a single pressure sensor (10); estimating the rotation speed of the motor (2) of the boosting system (1) based on the operating pressure value and the number of blades (Z) of the impeller of the pump; - based on the operating pressure value detected by the single pressure sensor (10), the hydraulic flow and the hydraulic head are estimated by an algorithm implemented in the control software, wherein when estimating the hydraulic head, the suction pressure (Hinf) is estimated using the nominal absolute pressure (Hmaxf) measured by the pressure sensor under operating conditions under zero flow conditions, the nominal absolute pressure (Hmaxnom) measured by the pressure sensor and the nominal absolute pressure of the suction (Hinnom); - generating an opening / closing signal for the pressure boosting system (1) according to the estimated hydraulic flow and hydraulic head.

2. The management and control method according to claim 1, It is characterized in that The step of generating an on / off signal of the boosting system (1) based on the estimated hydraulic flow and hydraulic head comprises an updating step: starting from the operating pressure value and the rotation speed of the motor, updating the value of the nominal hydraulic head of the nominal operating parameter of the boosting system (1).

3. The management and control method according to claim 2, It is characterized in that The step of generating an opening / closing signal of the boosting system (1) according to the estimated hydraulic flow and hydraulic head comprises the step of calculating optimal values ​​of the input and suction hydraulic heads of the boosting system (1) within a reference value range.

4. The management and control method according to claim 3, It is characterized in that The step of generating an opening / closing signal of the boosting system (1) according to the estimated hydraulic flow and hydraulic head comprises the steps of calculating the pressure variation between the input and suction hydraulic heads and the nominal hydraulic head, and the step of relatively optimizing the opening time of the boosting system (1) according to the opening / closing signal.

5. The management and control method according to claim 3, It is characterized in that The calculation of the optimal values ​​of the input and suction hydraulic heads of the boosting system (1) comprises the steps of: - setting the initial pressure parameters of the boosting system (1); - calibrating the boost system (1) by an iterative comparison process of the weighted difference in the operating hydraulic head and a preset reference value; - Identifying reference values ​​of said input and suction hydraulic heads and values ​​of minimum energy consumption conditions within a preset time period.

6. The management and control method according to claim 5, It is characterized in that It also includes iterative repetition of optimizing the energy consumption of the operation of the boosting system (1) and identifying the non-design operating conditions of the boosting system (1).

7. The management and control method according to claim 5, It is characterized in that This includes applying preset comfort parameters to the nominal hydraulic head value and the input and suction hydraulic head values.

8. A management and control method according to any one of the preceding claims, It is characterized in that It also includes a startup control step of the boosting system (1).

9. A management and control method according to any one of the preceding claims, It is characterized in that It also includes a step of estimating the volume of the expansion water tank according to the operating conditions of the boosting system (1), which is suitable for maintaining a preset minimum operating threshold for opening and closing the boosting system (1).

10. A pressure boosting system (1) comprising a pump with an impeller, a single pressure sensor (10) and an electronic control unit (4) adapted to perform the method according to any of the preceding claims.

11. The pressure boosting system (1) according to claim 10, further comprising an electric motor (2) of asynchronous type.

12. The pressure boosting system (1) according to claim 11, further comprising an expansion water tank.

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