EP4411205A1 - Procédé de commande du fonctionnement d'une installation de chauffage hybride pour chauffer un gaz et installation de chauffage hybride associée - Google Patents

Procédé de commande du fonctionnement d'une installation de chauffage hybride pour chauffer un gaz et installation de chauffage hybride associée Download PDF

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Publication number
EP4411205A1
EP4411205A1 EP23425004.1A EP23425004A EP4411205A1 EP 4411205 A1 EP4411205 A1 EP 4411205A1 EP 23425004 A EP23425004 A EP 23425004A EP 4411205 A1 EP4411205 A1 EP 4411205A1
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EP
European Patent Office
Prior art keywords
gas
heat pump
temperature
value
water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23425004.1A
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German (de)
English (en)
Inventor
Antoine Frein
Amedeo Cerio
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Enersem Srl
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Enersem Srl
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Publication date
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Priority to EP23425004.1A priority Critical patent/EP4411205A1/fr
Publication of EP4411205A1 publication Critical patent/EP4411205A1/fr
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/06—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/156—Reducing the quantity of energy consumed; Increasing efficiency
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/208—Temperature of the air after heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/212—Temperature of the water
    • F24H15/215—Temperature of the water before heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/238—Flow rate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/40—Control of fluid heaters characterised by the type of controllers
    • F24H15/414—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based
    • F24H15/421—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based using pre-stored data
    • F24H15/429—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based using pre-stored data for selecting operation modes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/06—Air heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/2064—Arrangement or mounting of control or safety devices for air heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/2064—Arrangement or mounting of control or safety devices for air heaters
    • F24H9/2085—Arrangement or mounting of control or safety devices for air heaters using fluid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/06—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators
    • F24H3/08—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by tubes
    • F24H3/081—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by tubes using electric energy supply
    • F24H3/085—The tubes containing an electrically heated intermediate fluid, e.g. water

Definitions

  • the present invention generally concerns the field of controlling the operation of a hybrid heating plant comprising a gas heating system and at least one heat pump.
  • the present invention concerns a method for controlling the setpoint temperature of the delivery water of the at least one heat pump.
  • Hybrid heating plants comprising a gas heating system consisting of one or more gas boilers (traditional or condensing ones) and one or more electrically or gas fed heat pumps are known.
  • the Applicant has observed that the hybrid heating plants used for gas decompression are not optimised in terms of energy consumption, as the gas boilers are oversized and therefore reduce the operating range of the heat pumps.
  • the present invention concerns a method for controlling the setpoint temperature of the delivery water of a heat pump of a hybrid heating plant used to heat a gas, wherein the control method is defined in the appended claim 1 and by preferred embodiments thereof described in dependent claims 2 to 10.
  • the method for controlling the setpoint temperature of the delivery water of the heat pump of the hybrid heating plant and relative hybrid heating plant according to the present invention has the advantage of optimising the energy consumption of the plant (for example in terms of gas consumption), maximizing the equivalent hours of operation at full speed of the heat pumps and maximizing the efficiency thereof, i.e. minimizing the minimum setpoint temperature of the delivery water of the heat pumps and stabilizing the switching from a maximum thermal power operating mode to a modulated thermal power operating mode and vice versa.
  • It is also an object of the present invention a computer program comprising software code portions adapted to perform the steps of the method for controlling the setpoint temperature of the delivery water of the heat pump of a hybrid heating plant according to the invention, when said program is run on at least one computer.
  • FIG. 1 a block diagram of a hybrid heating plant 1 according to an embodiment of the invention is shown.
  • the heating plant 1 comprises a gas boiler 4, a heat pump 3, a heat exchanger 5 and a gas pressure regulator 15.
  • the heating plant 1 further comprises two water temperature sensors 7 and 8, a gas temperature sensor 6, a water flow meter 19 and a control unit 10 electrically connected to the sensors 6, 7, 8 and to the water flow meter 19.
  • the heat pump 3 operates in combination (i.e. in parallel) with the gas boiler 4 in order to supply thermal power to the heat exchanger 5, by means of an appropriate control of the operation of the temperature of the delivery water of the heat pump 3, as will be explained in more detail below.
  • the heating plant 1 has the function of heating a gas flow before it is decompressed, in order to distribute it to civil and/or industrial users with an appropriate pressure value.
  • the heat exchanger 5 is thermally coupled with an inlet pipe 16 adapted to receive a gas flow from a gas distribution network and is thermally coupled with an outlet pipe 17 adapted to generate a heated gas flow.
  • the pressure regulator 15 is connected to the outlet pipe 17 and has the function of decompressing the heated gas, generating at the outlet a decompressed gas carried in a pipe 18 feeding civil and/or industrial users.
  • the case is considered in which the gas is heated to reduce its pressure with the aim of distributing the gas to civil or industrial users: in this case the gas boiler 4, the heat exchanger 5 and the pressure regulator 15 are enclosed within a same gas decompression cabin.
  • the gas boiler 4 comprises an inlet pipe 22 adapted to carry cold water received from the heat exchanger 5 and comprises an outlet pipe 23 adapted to carry hot water towards the heat exchanger 5.
  • the heat pump 3 comprises an inlet pipe 20 adapted to carry cold water received from the heat exchanger 5: the water flowing in the inlet pipe 20 will be hereinafter referred to as "return water” of the heat pump 3.
  • the heat pump 3 further comprises an outlet pipe 21 adapted to carry hot water towards the heat exchanger 5: the water flowing in the outlet pipe 21 will be hereinafter referred to as "delivery water” of the heat pump 3.
  • the heat pump 3 receives at the inlet from the control unit 10 a control signal carrying a value Tset_PdC of the setpoint (i.e. setting) temperature of the delivery water of the heat pump 3, thus the heat pump 3 modifies its operation so as to generate on the outlet pipe 21 a flow of delivery hot water having an actual temperature Tm_PdC chasing said value Tset_PdC of the setpoint temperature.
  • the heat pump 3 can be electrically powered, in the case of operation with compression of a fluid.
  • the heat pump may be fed with gas, in the case of absorption of heat from a fluid.
  • the heat exchanger 5 comprises an inlet pipe 25 adapted to carry hot water received from the assembly of the pipe 23 of the gas boiler 4 and of the pipe 21 of the heat pump 3.
  • the heat exchanger 5 further comprises an outlet pipe 24 adapted to carry cold water towards the pipe 22 of the gas boiler 4 and towards the heat pump pipe 20.
  • the heat exchanger 5 is for example a water/gas exchanger which receives at the inlet the hot water flowing through the inlet pipe 25 and generates at the outlet cold water flowing through the pipe 24: by means of the heat exchanger 5 heat is transferred from the hot water in the heat exchanger 5 to the gas, which is then heated and sent in the outlet pipe 17.
  • the water flowing in the outlet pipe 24 of the heat exchanger 5 will hereinafter be referred to as "return water” of the heat exchanger 5.
  • the heat exchanger may be a tube bundle, i.e. formed by a tube bundle placed inside a cylindrical-shaped container (called shell), in which a fluid (in particular, water) flows inside the tubes, while another fluid (in particular, gas) flows in the space delimited between the inner surface of the shell and the outer surfaces of the tubes, thus transferring heat between the two fluids.
  • a fluid in particular, water
  • another fluid in particular, gas
  • the water temperature sensor 8 is coupled to the pipe 24 at the outlet from the heat exchanger 5 and it has the function of detecting the temperature of the return water of the heat exchanger 5, i.e. the temperature of the cold water carried by the pipe 24 at the outlet from the heat exchanger 5, generating a water temperature signal Tr_w indicative of the temperature of the return water of the heat exchanger 5.
  • the temperature sensor 8 is coupled to the pipe 20 at the inlet to the heat pump 3 and has the function of detecting the temperature of the cold water carried by the pipe 20 at the inlet to the heat pump 3.
  • the temperature sensor 8 is coupled to the pipe 22 and has the function of detecting the temperature of the cold water carried by the pipe 22 at the inlet to the gas boiler 4.
  • the gas temperature sensor 6 has the function of detecting the current temperature of the decompressed gas flow in the pipe 18, generating a gas temperature signal T_gas indicative of the current temperature of the decompressed gas flow carried in the pipe 18.
  • the gas temperature sensor 6 can be mounted on the pipe 17 located directly at the outlet of the heat exchanger 5: in this case the gas temperature sensor 6 has the function of detecting the temperature of the heated gas flow carried by the pipe 17 directly connected at the outlet from the heat exchanger 5, i.e. before gas decompression.
  • the water temperature sensor 7 has the function of detecting the temperature of the delivery water of the gas boiler 4 (i.e. the temperature of the hot water carried by the pipe 23 connected at the outlet to the gas boiler 4), generating a further water temperature signal T_o_c indicative of the temperature of the delivery water of the gas boiler 4.
  • the temperature T_o_c of the delivery water of the gas boiler 4 is for example comprised between 40 degrees centigrade and 80 degrees centigrade.
  • the heating plant 1 comprises a water flow sensor 19 (inside or outside the heat pump 3) generating a water flow signal Fm_o_PdC indicative of the flow rate of the water associated with the heat pump 3, in particular the flow rate of the delivery water flowing in the pipe 21 at the outlet from the heat pump 3.
  • the control unit 10 has the function of controlling the operation of the heat pump 3 in combination with the gas boiler 4, in order to optimise the gas consumption of the plant 1, maximizing the operating hours of the heat pump 3 (i.e. maximizing the thermal power delivered by the heat pump 3) and maximizing its efficiency, since the minimum value of the setpoint temperature of the delivery water of the heat pump 3 is minimized and the switching of the heat pump 3 from the maximum thermal power to the modulated thermal power operating mode (and vice versa) is stabilized.
  • the control unit 10 is for example a microprocessor executing a suitable software program.
  • control unit 10 is a microcontroller or a PLC (Programmable Logic Controller).
  • the control unit 10 is electrically connected to the heat pump 3, to the water temperature sensors 7, 8, to the gas temperature sensor 6 and to the water flow meter 19.
  • control unit 10 comprises one or more inlet terminals adapted to receive the values measured by the sensors 8, 7, 6 and by the water flow meter 19, i.e. the water temperature signal Tr_w indicative of the temperature of the return water of the heat exchanger 5, the further water temperature signal T_o_c indicative of the temperature of the delivery water of the gas boiler 4, the gas temperature signal T_gas indicative of the current temperature of the decompressed gas carried in the pipe 18 and the water flow signal Fm_o_PdC indicative of the flow rate of the water associated with the heat pump 3 (for example, the delivery water).
  • the water temperature signal Tr_w indicative of the temperature of the return water of the heat exchanger 5
  • T_o_c indicative of the temperature of the delivery water of the gas boiler 4
  • gas temperature signal T_gas indicative of the current temperature of the decompressed gas carried in the pipe 18
  • the water flow signal Fm_o_PdC indicative of the flow rate of the water associated with the heat pump 3 (for example, the delivery water).
  • the control unit 10 further comprises an outlet terminal adapted to generate the control signal carrying the value Tset_PdC of the setpoint (i.e. setting) temperature of the delivery water of the heat pump 3, wherein said value Tset_PdC is used by the heat pump 3 to modify its operation in order to generate at the outlet delivery hot water having an actual temperature Tm_PdC chasing said value Tset_PdC.
  • the control unit 10 is configured to calculate the following internal variables, which will then be used to calculate the setpoint temperature Tset_PdC of the delivery water of the heat pump 3:
  • control unit 10 is configured to control the operation of the heat pump 3 so that it operates at least according to the following operating modes:
  • the hybrid heating plant 1 comprises two or more gas boilers analogous to the gas boiler 4 and/or two or more heat pumps analogous to the heat pump 3: in this case, therefore, two or more heat pumps operate in parallel to the two or more gas boilers.
  • the flowchart 100 is executed by means of a suitable software program (or firmware) executed on the control unit 10 of the hybrid heating plant 1.
  • the flowchart 100 is repeated at defined time intervals, in particular periodically, for example with an interval equal to 2 seconds.
  • the flowchart 100 starts with step 101.
  • Step 101 is followed by step 102 in which the values indicative of the temperature of the return water Tr_w of the heat exchanger 5, of the temperature of a gas T_gas to be decompressed or decompressed and of the flow rate of the water Fm_o_PdC associated with the heat pump 3 are acquired at a certain time instant.
  • step 102 the switched on or off operating state of the gas boiler 4 (operating in parallel with the heat pump 3) is detected in the last period of time, i.e. in a defined time interval preceding the determined time instant in which the data from the sensors indicated above were acquired.
  • step 102 the operating state of the heat pump 3 is acquired.
  • the switched on or off operating state of the gas boiler 4 can be detected for example by detecting the temperature of the water at the outlet from the gas boiler 4 (i.e. the temperature of the delivery water T_o_c of the gas boiler 4, i.e. the temperature of the water carried by the pipe 23 at the outlet from the gas boiler 4) and by detecting the temperature of the water at the inlet to the gas boiler 4.
  • the switched on/off operating state of the gas boiler 4 is detected by comparing the difference between the temperature of the water at the outlet from the gas boiler 4 (i.e. the temperature T_o_c of the delivery water of the gas boiler 4) and the temperature of the water at the inlet to the gas boiler 4 (i.e. the temperature of the water in the pipe 22 at the inlet of the gas boiler 4 or in the pipe 24 at the outlet from the heat exchanger 5) and a value of a boiler activation temperature threshold (for example, 4 degrees centigrade):
  • the switched on/off state of the gas boiler 4 can be detected by means of a magnetometer, a magnetic field meter, a vibration tester or by connecting with the regulator inside the gas boiler 4 and retrieving its operating state.
  • Step 102 is followed by step 103 in which it is checked whether the heat pump 3 is active:
  • the active or inactive operating state of the heat pump 3 is updated (see next steps 104 and 105) as a function of the temperature of the gas T_gas with respect to the first setpoint temperature value of the gas T1_set_gas (see next step 104) and as a function of the temperature of the gas T_gas with respect to the second setpoint temperature value of the gas T2_set_gas (see next step 105).
  • step 104 it is checked whether the value of the temperature of the gas T_gas (decompressed or to be decompressed) is lower than a first setpoint temperature value of the gas T1_set_gas (for example, T1_set_gas is equal to 12 degrees centigrade):
  • step 105 it is checked whether the value of the temperature of the gas T_gas (decompressed or to be decompressed) is lower than a second setpoint temperature value of the gas T2_set_gas lower than the first setpoint temperature value of the gas (for example, equal to 10 degrees centigrade):
  • T1_set_gas T2_set_gas of the setpoint temperature of the gas defines a hysteresis having the advantage of reducing the frequency of the switching on or off of the gas boiler 4.
  • step 106 it is checked whether the gas boiler 4 has always been switched off in the last period of time (i.e. in a defined time interval preceding the time instant in which the values from the temperature sensors were acquired):
  • step 107 it is checked whether the gas boiler 4 has always been switched off in the last period of time (i.e. in a defined time interval preceding the time instant in which the values from the temperature sensors were acquired):
  • step 108 the heat pump 3 operates at a maximum thermal power mode in which the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 chases a maximum value Tset_PdC_max of the setpoint temperature of the delivery water varying over time, as shown in Figures 4A (line 202) and 4B (line 202a).
  • a maximum value Tset_PdC_max of the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 is calculated as a function of the temperature of the return water Tr_w of the heat exchanger 5 and of the flow rate of the water Fm_o_PdC associated with the heat pump 3, then said calculated maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 is set.
  • the calculated maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 has values comprised between 45 and 53 degrees centigrade and is continuously updated as a function of the temperature of the value of the return water Tr_w of the heat exchanger 5 and of the flow rate of the water Fm_o_PdC associated with the heat pump 3.
  • said calculation and setting of the maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 is carried out by means of the control unit 10, which generates the control signal Tset_PdC equal to the calculated maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3, which receives said calculated maximum value Tset_PdC_max in input and modifies its operation so as to generate on the outlet pipe 21 a delivery hot water flow having an actual temperature Tm_PdC chasing said calculated maximum value Tset_PdC_max.
  • Step 108 will be explained in more detail below with reference to the description of Figure 3 .
  • step 109 the heat pump 3 operates at a modulated thermal power mode in which the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 varies over time and is comprised between a minimum value Tset_PdC_min and the maximum value Tset_PdC_max, as shown in Figure 5A .
  • a variation over time of the value of the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 is calculated as a function of an acquired value of the temperature of the gas T_gas and of a value of a regulation setpoint temperature of the gas Treg_set_gas, wherein said variation is comprised between a minimum value Tset_PdC_min and the maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 (the latter calculated in step 108), then said variation over time of the calculated value of the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 is set.
  • step 108 in which the heat pump 3 operates at maximum power in the case in which the temperature of the (decompressed or to be decompressed) gas is low and furthermore the gas boiler 4 has been switched on (at least in part) in the considered last period of time.
  • step 109 in which the heat pump 3 operates with a fine variation of the power delivered between a minimum and maximum value that are variable over time, in the case in which the temperature of the (decompressed or to be decompressed) gas is low and furthermore the gas boiler 4 has always been switched off in the considered last period of time.
  • step 109 in particular the calculation of the maximum value T_set_PdC_max of the setpoint temperature of the delivery water will be explained in more detail below with reference to the description of Figure 3 .
  • step 110 the heat pump 3 is set in a stand-by state, by setting the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 to a sufficiently low value (for example, equal to 20 degrees centigrade), in which the heat pump 3 is active but does not consume gas or electricity.
  • a sufficiently low value for example, equal to 20 degrees centigrade
  • step 111 the heat pump 3 is switched off, by setting the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 to a very low value (for example, equal to about 0 degrees centigrade).
  • step 110 we arrive at step 110 in which the heat pump 3 is in a stand-by state in the case in which the temperature of the (decompressed or to be decompressed) gas is high and furthermore the gas boiler 4 has been switched on (at least in part) in the last period of time considered; otherwise, we arrive at step 111 in which the heat pump 3 is switched off, in the case in which the temperature of the (decompressed or to be decompressed) gas is high and furthermore the gas boiler 4 has always been switched off in the last period of time considered.
  • the flow rate of the water associated with the two or more heat pumps is acquired in step 101 and the switched on or off operating state of the two or more heat pumps is acquired.
  • step 102 the active or inactive operating state of the two or more heat pumps is detected and in step 103 it is checked whether at least one heat pump is active.
  • steps 106 and 107 it is checked whether all two or more gas boilers have always been switched off in the last period of time.
  • step 108 the maximum value of the setpoint temperature of the delivery water for the two or more heat pumps is set and in step 109 the variation over time of the calculated value of the setpoint temperature of the delivery water for the two or more heat pumps is set.
  • step 102 From steps 108, 109, 110 and 111 a return to step 102 is made and the data acquisition cycle of the sensors, the calculation of the setpoint temperature of the delivery water of the heat pump, the acquisition of the operating state of the heat pump 3 and the gas boiler 4 are started again.
  • FIG. 3 shows a flowchart 150 of the method for calculating the maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 of the hybrid heating plant 1, when the heat pump 3 operates at the maximum thermal power mode (step 108 illustrated above) or when the heat pump 3 operates at the modulated thermal power mode (step 109 illustrated above).
  • the maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 is used when the heat pump 3 operates at the modulated thermal power mode (step 109 illustrated above) to define the maximum value of the temperature modulation interval of the delivery water of the heat pump 3.
  • the flowchart 150 shows in more detail step 108 and a part of step 109 of the flowchart 100 of Figure 2B .
  • the flowchart 150 is executed by means of a suitable software program (or firmware) executed on the control unit 10 of the plant 1.
  • the flowchart 150 starts with step 151.
  • Step 151 is followed by step 152 in which a plurality of values of a statistical index of the temperature of the return water Tr_w of the heat exchanger 5 are calculated in a respective plurality of defined time intervals.
  • the statistical index is for example the mean, the mode or the median.
  • Step 152 is followed by step 153 in which it is checked whether the current value of the temperature of the return water Tr_w of the heat exchanger 5 is lower than the set value of a setpoint temperature of the return water of the heat exchanger 5:
  • step 154 the trend of the plurality of calculated values of the statistical index of the temperature of the return water is analysed as the respective plurality of defined time intervals vary:
  • step 155 the trend of the plurality of calculated values of the statistical index of the temperature of the return water is analysed as the respective plurality of defined time intervals vary:
  • step 156 the maximum value of the setpoint temperature Tset_PdC_max of the delivery water of the heat pump 3 is decreased.
  • step 156 the value of the setpoint temperature of the return water of the heat exchanger 5 is decreased as a function of the objective power of the heat pump 3 and of the flow rate of the water Fm_or_PdC associated with the heat pump 3.
  • step 156 From step 156 a return to step 152 is made and the calculation method starts over as illustrated above.
  • the objective power of the heat pump 3 is a specific value of the heat pump 3 and is chosen as a function of the particular operating conditions.
  • the power delivered by the heat pump 3 decreases, thus the objective power of the heat pump 3 is slightly lower than the nominal power of the heat pump 3.
  • step 157 the maximum value of the setpoint temperature Tset_PdC_max of the delivery water of the heat pump 3 is increased.
  • step 157 the value of the setpoint temperature of the return water of the heat exchanger 5 is increased as a function of the objective power of the heat pump 3 and of the flow rate of the water Fm_o_PdC.
  • step 157 a return to step 152 is made and the calculation method starts over as illustrated above.
  • the maximum value of the setpoint temperature Tset_PdC_max of the delivery water of the heat pump 3 has thus a variable value over time, both when the heat pump 3 operates at the modulated power mode (see dashed line 212 of Figure 5A and the solid line 222 of Figure 5B ), and when this operates at the maximum power mode (see line 202 in Figure 4A and line 202a in Figure 4B ).
  • step 156 the maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 is further decreased by further taking into consideration the past values of the temperature of the return water Tr_w of the heat exchanger 5 and in step 157 the maximum value Tset_PdC_max of the setpoint temperature is further increased by further taking into consideration the past values of the temperature of the return water Tr_w.
  • the heat pump 3 operates at constant flow rate: in this case in steps 156 and 157 the value of the setpoint temperature of the return water of the heat exchanger 5 is updated only as a function of the value ⁇ T_in_out of the desired water temperature difference between the inlet pipe 20 and the outlet pipe 21 of the heat pump 3, which in turn depends on the desired power and on the flow rate of the heat pump 3.
  • step 158 the maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 is kept unchanged.
  • the flowchart 150 is repeated at defined time intervals, for example periodically, in order to dynamically update over time the maximum value Tset_Pdc_max of the setpoint temperature of the delivery water of the heat pump 3.
  • the calculation method illustrated above relating to the maximum value of the setpoint temperature of the delivery water of the heat pump 3 has the advantage of minimizing the operating instability caused by the discontinuous activation of the gas boiler 4.
  • the value of the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 varies between a minimum value Tset_PdC_min and the maximum value Tset_PdC_max, as shown by the solid line 210 of Figure 5A .
  • the value of the setpoint temperature Tset_PdC of the delivery water of the heat pump 3 is regulated by means of a Proportional-Integrative type controller which receives the value of the temperature of the gas T_gas in input and makes a comparison with a value of a setpoint regulation temperature of the gas Treg_set_gas.
  • the minimum and maximum value of the setpoint temperature of the delivery water of the heat pump 3 are variable over time and therefore define a moving band within which the Proportional-Integrative controller operates.
  • the Proportional-Integrative type controller is realized by means of a suitable software program executed in the control unit 10.
  • the minimum setpoint value of the temperature of the delivery water of the heat pump 3 of the hybrid heating plant 1 is calculated with the following algorithm:
  • the calculation of the minimum value of the setpoint temperature of the delivery water of the heat pump 3 is carried out by means of a suitable software program executed by the control unit 10.
  • FIGS 4A and 4B show a possible trend over time of the maximum value Tset_PdC_max of the setpoint temperature (measured in degrees centigrade) of the delivery water of the heat pump 3 (line 202 and 202a), of the actual temperature Tm_PdC of the delivery water of the heat pump 3 (line 201) and of the actual temperature of the return water Tr_w of the heat exchanger 5 (line 203), when the heat pump 3 operates at the maximum thermal power mode.
  • the maximum value Tset_PdC_max (indicated with a solid line with reference numbers 202 and 202a) of the setpoint temperature of the delivery water of the heat pump 3 has a variable trend over time comprised between 45-46 degrees centigrade and 52-53 degrees centigrade.
  • the trend of the actual temperature Tm_PdC of the delivery water of the heat pump 3 chases the trend of the maximum value Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 as the time varies, except for small differences in values which are caused by the instability of the temperature of the return water Tr_w of the heat exchanger 5.
  • the actual temperature of the return water Tr_w of the heat exchanger 5 has an oscillating trend similar to the oscillating trend of the actual temperature Tm_PdC of the delivery water of the heat pump 3, wherein the values of the actual temperature of the return water Tr_w are always lower than the corresponding values of the actual temperature Tm_PdC of the delivery water.
  • a first possible trend of the setpoint temperature T_set_PdC of the delivery water of the heat pump 3 (line 210), of the minimum value Tset_PdC_min (line 211) of the setpoint temperature of the delivery water of the heat pump 3 and of the maximum value Tset_PdC_max (line 212) of the setpoint temperature of the delivery water of the heat pump 3 is shown, when this operates at the modulated thermal power mode.
  • the values of the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 (line 210) when the time varies at each instant are comprised (at the equal limit) between the respective minimum values Tset_PdC_min (line 211) and maximum values Tset_PdC_max (line 212) of the setpoint temperature of the delivery water of the heat pump 3, wherein said minimum values Tset_PdC_min and maximum values Tset_PdC_max of the setpoint temperature of the delivery water of the heat pump 3 vary dynamically over time, as illustrated above.
  • Figure 5A shows that at instant t10 the value of the setpoint temperature of the delivery water Tset_PdC of the heat pump 3 is equal to 42 degrees centigrade, which is comprised between the minimum value of the setpoint temperature equal to 35 degrees centigrade and the maximum value of the setpoint temperature equal to 49 degrees centigrade.
  • the heat pump 3 switches from the maximum thermal power operating mode to the modulated thermal power operating mode and at switching instant t21 the minimum value Tset_PdC_min of the setpoint temperature Tset_PdC of the delivery water of the heat pump 3 is equal to the maximum value Tset_PdC_max of the setpoint temperature Tset_PdC of the delivery water of the heat pump 3.
  • the minimum value Tset_PdC_min (line 221) of the setpoint temperature of the delivery water of the heat pump 3 gradually decreases, until at instant t22 the minimum value Tset_PdC_min is equal to the difference between the maximum value Tset_PdC_max (line 222) of the setpoint temperature of the delivery water of the heat pump 3 and the desired temperature difference ⁇ T_in_out of the water between the inlet and the outlet of the heat pump: therefore at the instants subsequent to t22 the trend of the maximum value Tset_PdC_max (line 222) is equal to the sum of the trend of the minimum value Tset_PdC_min (line 221) and of the value ⁇ T_in_out of the desired temperature difference of the water between the inlet and the outlet of the heat pump 3.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Computer Hardware Design (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
EP23425004.1A 2023-02-02 2023-02-02 Procédé de commande du fonctionnement d'une installation de chauffage hybride pour chauffer un gaz et installation de chauffage hybride associée Pending EP4411205A1 (fr)

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EP23425004.1A EP4411205A1 (fr) 2023-02-02 2023-02-02 Procédé de commande du fonctionnement d'une installation de chauffage hybride pour chauffer un gaz et installation de chauffage hybride associée

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EP23425004.1A EP4411205A1 (fr) 2023-02-02 2023-02-02 Procédé de commande du fonctionnement d'une installation de chauffage hybride pour chauffer un gaz et installation de chauffage hybride associée

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012160433A1 (fr) * 2011-05-23 2012-11-29 Angelo Mapelli Système de chauffage de gaz pour systèmes de réduction de pression de gaz et procédé d'obtention dudit effet de chauffage
US9341383B2 (en) * 2010-12-08 2016-05-17 Daikin Industries, Ltd. Heating system and method for controlling a heating system
US10677392B2 (en) * 2015-12-02 2020-06-09 Nuovo Pignone Srl Control system and method for pressure-let-downs stations
US20220252326A1 (en) * 2021-02-08 2022-08-11 A. O. Smith (China) Water Heater Co., Ltd. Defrosting control method, central controller and heating system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9341383B2 (en) * 2010-12-08 2016-05-17 Daikin Industries, Ltd. Heating system and method for controlling a heating system
WO2012160433A1 (fr) * 2011-05-23 2012-11-29 Angelo Mapelli Système de chauffage de gaz pour systèmes de réduction de pression de gaz et procédé d'obtention dudit effet de chauffage
US10677392B2 (en) * 2015-12-02 2020-06-09 Nuovo Pignone Srl Control system and method for pressure-let-downs stations
US20220252326A1 (en) * 2021-02-08 2022-08-11 A. O. Smith (China) Water Heater Co., Ltd. Defrosting control method, central controller and heating system

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