EP3115707B1 - Dispositif source de chaleur - Google Patents

Dispositif source de chaleur Download PDF

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Publication number
EP3115707B1
EP3115707B1 EP15751873.9A EP15751873A EP3115707B1 EP 3115707 B1 EP3115707 B1 EP 3115707B1 EP 15751873 A EP15751873 A EP 15751873A EP 3115707 B1 EP3115707 B1 EP 3115707B1
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EP
European Patent Office
Prior art keywords
heat
heat source
transfer medium
water
flow
Prior art date
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EP15751873.9A
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German (de)
English (en)
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EP3115707A1 (fr
EP3115707A4 (fr
Inventor
Yuuji Matsumoto
Seiji Tsukiyama
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Toshiba Carrier Corp
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Toshiba Carrier Corp
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Publication of EP3115707A4 publication Critical patent/EP3115707A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/85—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using variable-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/003—Indoor unit with water as a heat sink or heat source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/06—Several compression cycles arranged in parallel

Definitions

  • the heat source unit takes in a heat-transfer medium (water or brine) by the operation of a pump, and heats or cools the taken-in heat-transfer medium by the operation of a heat-pump-type refrigerating cycle.
  • a heat-transfer medium water or brine
  • Each of the air heat exchangers 3a, 3b, ... 3n exchanges the heat of the water flowing from the water pipe 2a with the heat of indoor air sent from an indoor fan, and discharges the water after this heat exchange to the water pipe 2b.
  • a flow sensor (a flow detect section) 5 is arranged in the water pipe 2b.
  • the flow sensor 5 detects the amount (total volume) of water flowing from the air heat exchangers 3a, 3b, ... 3n as an amount (total volume) of water Qt which flows into the air heat exchangers 3a, 3b, ... 3n.
  • bypass pipe 6 causes the water flowing from the heat source units 1a, 1b, ... In toward the air heat exchangers 3a, 3b, ... 3n to bypass the air heat exchangers 3a, 3b, ... 3n, and be returned to the heat source units 1a, 1b, ... 1n.
  • a flow control valve (a second flow control valve) 7 the degree of opening of which is variable, is provided.
  • the flow control valve 7 is also called a bypass valve, and the amount of water which flows into the bypass pipe 6 can be controlled by a change in the degree of opening of the flow control valve 7.
  • a differential pressure sensor 8 which is a first differential pressure detect section, is connected.
  • the differential pressure sensor 8 detects a difference P between the pressure of water on one end of the bypass pipe 6 and the pressure of water on the other end of the same (i.e., a difference P between water pressures at both ends of the bypass pipe 6).
  • FIG. 2 shows the structure of a heat-pump-type refrigerating cycle mounted in the heat source unit 1a. Note that each of the heat-pump-type refrigerating cycles mounted in the heat source units 1b, ... 1n also has a similar structure.
  • the direction in which the refrigerant flows as above corresponds to one at the time of a cooling operation (a cold-water generation operation), and the air heat exchangers 23a and 23b serve as condensers, and the first refrigerant channel 30a of the water heat exchanger 30 serves as an evaporator.
  • a cooling operation a cold-water generation operation
  • the channel of the four-way valve 22 is switched and the flowing direction of the refrigerant is reversed. That is, the first refrigerant channel 30a of the water heat exchanger 30 serves as the condenser, and the air heat exchangers 23a and 23b serve as the evaporators.
  • a first heat-pump-type refrigerating cycle is constituted by the compressor 21, the four-way valve 22, the air heat exchangers 23a and 23b, the electronic expansion valves 24a and 24b, the first refrigerant channel 30a of the water heat exchanger 30, and the accumulator 25.
  • the direction in which the refrigerant flows as above corresponds to one at the time of a cooling operation (a cold-water generation operation), and the air heat exchangers 43a and 43b serve as condensers, and the second refrigerant channel 30b of the water heat exchanger 30 serves as an evaporator.
  • a cooling operation a cold-water generation operation
  • the channel of the four-way valve 42 is switched and the flowing direction of the refrigerant is reversed. That is, the second refrigerant channel 30b of the water heat exchanger 30 serves as the condenser, and the air heat exchangers 43a and 43b serve as the evaporators.
  • the direction in which the refrigerant flows as above corresponds to one at the time of a cooling operation (a cold-water generation operation), and the air heat exchangers 53a and 53b serve as condensers, and the first refrigerant channel 60a of the water heat exchanger 60 serves as an evaporator.
  • a cooling operation a cold-water generation operation
  • the air heat exchangers 53a and 53b serve as condensers
  • the first refrigerant channel 60a of the water heat exchanger 60 serves as an evaporator.
  • the channel of the four-way valve 52 is switched and the flowing direction of the refrigerant is reversed. That is, the first refrigerant channel 60a of the water heat exchanger 60 serves as the condenser, and the air heat exchangers 53a and 53b serve as the evaporators.
  • a third heat-pump-type refrigerating cycle is constituted by the compressor 51, the four-way valve 52, the air heat exchangers 53a and 53b, the electronic expansion valves 54a and 54b, the first refrigerant channel 60a of the water heat exchanger 60, and the accumulator 55.
  • the direction in which the refrigerant flows as above corresponds to one at the time of a cooling operation (a cold-water generation operation), and the air heat exchangers 73a and 73b serve as condensers, and the second refrigerant channel 60b of the water heat exchanger 60 serves as an evaporator.
  • a cooling operation a cold-water generation operation
  • the channel of the four-way valve 72 is switched and the flowing direction of the refrigerant is reversed. That is, the second refrigerant channel 60b of the water heat exchanger 60 serves as the condenser, and the air heat exchangers 73a and 73b serve as the evaporators.
  • a fourth heat-pump-type refrigerating cycle is constituted by the compressor 71, the four-way valve 72, the air heat exchangers 73a and 73b, the electronic expansion valves 74a and 74b, the second refrigerant channel 60b of the water heat exchanger 60, and the accumulator 75.
  • a pump 80 is provided in the water pipe 101.
  • the pump 80 draws the water within the water pipe 2b into the water pipe 101, and sends the drawn water to the water pipe 2b through the water heat exchanger 60, the water pipe 102, the water heat exchanger 30, and a water pipe 103.
  • the pump 80 has a motor which operates by an alternating voltage supplied from an inverter 81, and the power (lifting height) is changed in accordance with a speed of rotation of the motor.
  • the inverter 81 rectifies a voltage of a commercial alternating-current power supply 82, converts a direct-current voltage after the rectification into an alternating voltage of a predetermined frequency by switching, and supplies the converted alternating voltage as power to drive the motor of the pump 80.
  • a frequency (output frequency) F of an output voltage of the inverter 81 the speed of rotation of the motor of the pump 80 is changed.
  • a differential pressure sensor 90 which is a second differential pressure detect section, is connected.
  • the differential pressure sensor 90 detects a difference Pw between the pressure of water which flows into the water heat exchanger 60 and the pressure of water which flows out of the water heat exchanger 30.
  • the amount of water which flows into the water heat exchangers 60 and 30, that is, an amount of water Wa which flows into the heat source unit 1a, can be detected based on the pressure difference Pw detected by the differential pressure sensor 90.
  • a controller 10 is connected to the heat source units 1a, 1b, ... 1n, the flow control valves 4a, 4b, ... 4n, the flow sensor 5, the flow control valve 7, and the differential pressure sensor 8.
  • a heat source apparatus is constituted by the heat source units 1a, 1b, ... 1n, the water pipes 2a and 2b, the flow control valves 4a, 4b, ... 4n, the flow sensor 5, the bypass pipe 6, the flow control valve 7, the differential pressure sensor 8, and the controller 10.
  • the controller 10 controls the operation of the heat source units 1a, 1b, ... 1n, the degree of opening of the flow control valves 4a, 4b, ... 4n, and the degree of opening of the flow control valve 7.
  • the controller 10 includes a first detect section 11, a second detect section 12, a first control section 13, a second control section 14, a third control section 15, and a memory 16.
  • the second control section 14 controls the degree of opening of the flow control valve (bypass valve) 7 in accordance with the flow rate Qt detected by the flow sensor 5, and the load-side pipe resistance characteristic detected by the first detect section 11, so that an optimum amount of water which is commensurate with the total sum of the required power of each of the air heat exchangers 3a, 3b, ... 3n flows into the air heat exchangers 3a, 3b, ... 3n.
  • the third control section 15 divides (for example, equally divides) the flow rate Qt detected by the flow sensor 5 and allocates the divided flow rate to the heat source units in operation of the heat source units 1a, 1b, ... 1n as a necessary flow rate Wt. In this way, the third control section 15 controls the power of the pump 80 (the capability of supplying the heat-transfer medium) of each of the heat source units in operation so that each of the flow rates W detected by the second detect section 12 agrees with the allocated flow rate Wt.
  • the air heat exchangers 3n As the air heat exchanger having the greatest pipe resistance, the air heat exchangers 3n, for example, which is located at a distal end position where the distance of the pipe from the heat source units 1a, 1b, ... 1n is the greatest, is selected in advance.
  • the air heat exchanger 3b for example, which is closer to the heat source units 1a, 1b, ... 1n than from the air heat exchanger 3n at the distal end position, may be selected in advance as the air heat exchanger having the greatest pipe resistance for the fact that the branch pipes 2ab and 2bb connected to the water pipes 2a and 2b are narrower than the branch pipes of the other air heat exchangers. Selection of the air heat exchanger having the greatest pipe resistance is carried out based on an empirical rule or measurement of an operator in the installation of the heat source apparatus. A result of this selection is stored in the memory 16 of the controller 10.
  • the controller 10 controls the number of heat source units 1a, 1b, ... 1n to be operated, and the degree of opening of each of the flow control valves 4a, 4b, ... 4n (step S3).
  • the amount (total volume) of water Qt which actually flows into the air heat exchangers 3a, 3b, ... 3n is detected by the flow sensor 5.
  • the controller 10 obtains a target pressure difference Pt which is the target difference between water pressures at both ends of the bypass pipe 6 corresponding to the flow rate Qt detected by the flow sensor 5 from the load-side pipe resistance characteristic shown in FIG. 4 which has been detected and stored at the time of test operation (step S4). Further, the controller 10 controls the degree of opening of the flow control valve 7 (the bypass amount of water) such that the pressure difference P detected by the differential pressure sensor 8 (difference P between water pressures at both ends of the bypass pipe 6) is equivalent to the target pressure difference Pt obtained as described above (step S5).
  • step S7 By a computation based on the pressure difference Pw detected by the differential pressure sensor 90 of one or more heat source units in operation and the heat exchanger resistance characteristic of the water heat exchangers (the water heat exchangers 60 and 30) of the one or more heat source units in operation, the amount of water W which flows into the one or more heat source units in operation individually is detected (step S7).
  • the controller 10 when two heat source units, i.e., the heat source units 1a and 1b, are in operation, the controller 10 reads a pressure difference Pwa detected by the differential pressure sensor 90 of the heat source unit 1a and a pressure difference Pwb detected by the differential pressure sensor 90 of the heat source unit 1b, and also reads the heat exchanger resistance characteristic of the heat source unit 1a and the heat exchanger resistance characteristic of the heat source unit 1b from the memory 16. Then, the controller 10 detects an amount of water Wa which flows into the heat source unit 1a and an amount of water Wb which flows into the heat source unit 1b by a computation based on the detected pressure differences Pwa and Pwb and each of the heat exchanger resistance characteristics.
  • the controller 10 controls the output frequency F of each of the inverters 81 of the heat source units 1a and 1b such that each of the detected flow rates Wa and Wb agrees with the necessary flow rates Wt allocated to the heat source units 1a and 1b (step S8).
  • the controller 10 increases the output frequency F of the inverter 81 of the heat source unit 1a. As a result, the power of the pump 80 of the heat source unit 1a is increased, and the amount of water Wa which flows into the heat source unit 1a changes to be increased.
  • the controller 10 reduces the output frequency F of the inverter 81 of the heat source unit 1a. As a result, the power of the pump 80 of the heat source unit 1a is reduced, and the amount of water Wa which flows into the heat source unit 1a changes to be reduced.
  • the controller 10 maintains the output frequency F of the inverter 81 of the heat source unit 1a at that time.
  • FIG. 5 shows the relationship between the amounts of water Wa and Wn which flow into the heat source units 1a and 1n and the power (pumping power) of each of the pumps 80 of the heat source units 1a and 1n, when, for example, two heat source units 1a and 1n are operated, with the heat exchanger resistances Ra and Rn of the heat source units 1a and 1n given as the parameters.
  • the operating frequency F of the pump 80 of the heat source unit 1a may be set to a predetermined value Fa.
  • the above embodiment was described by referring to the heat source units 1a, 1b, ... 1n each comprising four heat-pump-type refrigerating cycles and two water heat exchangers as an example.
  • the numbers of heat-pump-type refrigerating cycles and water heat exchangers of each heat source unit can be selected as required.
  • the unit on the load side is an air heat exchanger.
  • the present embodiment can similarly be put into practice in a case where the unit on the load side is, for example, a hot-water storage tank.
  • an amount of water which flows to the load side is detected, the detected flow rate is evenly divided, and the divided flow rate is allocated to each of the heat source units in operation.
  • the division may not necessarily be even, but may be such a division that each of the pumps 80 can operate continuously without slowing down.
  • the load-side pipe resistance characteristic is detected through a test operation after installation of the heat source apparatus.
  • detecting the load-side pipe resistance characteristic is not limited to the above occasion, and may be carried out at the time of a test operation which takes place after the air heat exchangers on the load side have been increased or decreased.
  • the heat source apparatus of the present embodiment can be used for an air conditioner, a hot-water supply apparatus, etc.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Air Conditioning Control Device (AREA)
  • Other Air-Conditioning Systems (AREA)

Claims (9)

  1. Appareil source de chaleur comprenant :
    une pluralité d'unités source de chaleur (1a, 1b, ... 1n) qui comprennent chacune un échangeur de chaleur de fluide caloporteur (60) et sont configurées pour chauffer ou refroidir un fluide caloporteur au moyen de l'échangeur de chaleur de fluide caloporteur (60) et alimenter, avec le fluide caloporteur qui a chauffé ou refroidi, un côté charge ;
    une première vanne de réglage de débit (4a) configurée pour régler une quantité du fluide caloporteur qui s'écoule vers le côté charge ;
    une section de détection de débit (5) configurée pour détecter la quantité (Qt) du fluide caloporteur qui s'écoule vers le côté charge ;
    une conduite de dérivation (6) configurée pour dériver le fluide caloporteur qui s'écoule vers le côté charge ;
    une seconde vanne de réglage de débit (7) configurée pour régler une quantité du fluide caloporteur qui s'écoule dans la conduite de dérivation (6) ;
    caractérisé en ce que l'appareil source de chaleur comprend en outre :
    une première section de détection de pression différentielle (8) configurée pour détecter une différence de pression (P) entre les pressions du fluide caloporteur aux deux extrémités de la conduite de dérivation (6) ;
    des secondes sections de détection de pression différentielle (90) configurées pour détecter des différences de pression (Pw) entre les pressions du fluide caloporteur aux deux extrémités des échangeurs de chaleur de fluide caloporteur (60) ; et
    un contrôleur (10) qui comprend une première section de détection (11), une seconde section de détection (12), une première section de commande (13), une deuxième section de commande (14) et une troisième section de commande (15) ;
    la première section de détection (11) détecte une caractéristique de résistance de conduite côté charge représentant une relation entre une quantité (Q) du fluide caloporteur qui s'écoule vers le côté charge et une différence de pression (P) entre les pressions du fluide caloporteur aux deux extrémités de la conduite de dérivation (6) ;
    la seconde section de détection (12) détecte une quantité (W) du fluide caloporteur qui s'écoule dans chacune des unités source de chaleur (1a, 1b, ... 1n) en fonctionnement sur la base de la différence de pression (Pw) détectée par chacune des secondes sections de pression différentielle (90) ;
    la première section de commande (13) commande le nombre d'unités source de chaleur (1a, 1b, ... 1n) à actionner et la quantité d'ajustements de la vanne de réglage de débit (4a) en fonction de la capacité requise par le côté charge ;
    la deuxième section de commande (14) commande la quantité d'ajustements de la seconde vanne de réglage de débit (7) en fonction d'un débit (Qt) détecté par la section de détection de débit (5) et de la caractéristique de résistance de conduite côté charge détectée par la première section de détection (11) ; et
    la troisième section de commande (15) divise le débit (Qt) détecté par la section de détection de débit (5) et attribue le débit divisé aux unités source de chaleur (1a, 1b, ... 1n) en fonctionnement en tant que débit nécessaire (Wt) et commande une capacité à alimenter, avec le fluide caloporteur, chacune des unités source de chaleur (1a, 1b, ... 1n) en fonctionnement en fonction du débit nécessaire attribué (Wt).
  2. Appareil source de chaleur selon la revendication 1, caractérisé en ce que chacune des unités source de chaleur comprend :
    un cycle de réfrigération de type à pompe à chaleur configuré pour chauffer ou refroidir le fluide caloporteur à l'intérieur de l'échangeur de chaleur de fluide caloporteur (60) ; et
    une pompe (80) configurée pour aspirer le fluide caloporteur qui a traversé le côté charge et envoyer le fluide caloporteur aspiré vers le côté charge par l'intermédiaire de l'échangeur de chaleur de fluide caloporteur (60).
  3. Appareil source de chaleur selon la revendication 2, caractérisé en ce que :
    la première vanne de réglage de débit (4a) commande la quantité du fluide caloporteur qui s'écoule vers le côté charge par un changement d'un degré d'ouverture ;
    la conduite de dérivation (6) dérive le fluide caloporteur s'écoulant à partir de chacune des unités source de chaleur (1a, 1b, ..., 1n) vers le côté charge et renvoie le fluide caloporteur dérivé vers chacune des unités sources de chaleur (1a, 1b, ..., 1n) ; et
    la seconde vanne de réglage de débit (7) commande la quantité du fluide caloporteur qui s'écoule dans la conduite de dérivation (6) par un changement d'un degré d'ouverture.
  4. Appareil source de chaleur selon la revendication 3, caractérisé en ce que :
    la première section de commande (13) commande le nombre d'unités source de chaleur (1a, 1b, ..., 1n) à actionner et le degré d'ouverture de la première vanne de réglage de débit (4a) en fonction de la capacité requise par le côté charge ; et
    la deuxième section de commande (13) commande le degré d'ouverture de la seconde vanne de réglage de débit (7) en fonction du débit (Qt) détecté par la section de détection de débit (5) et de la caractéristique de résistance de conduite côté charge détectée par la première section de détection (11).
  5. Appareil source de chaleur selon la revendication 1, caractérisé en ce que les unités source de chaleur (1a, 1b, ..., 1n) sont reliées en parallèle les unes aux autres par une conduite.
  6. Appareil source de chaleur selon la revendication 1, caractérisé en ce que la première section de détection (11) détecte la caractéristique de résistance de conduite côté charge lors d'une opération de test.
  7. Appareil source de chaleur selon la revendication 1, caractérisé en ce que la seconde section de détection (12) détecte la quantité W (W) du fluide caloporteur qui s'écoule dans chacune des unités source de chaleur (1a, 1b, ..., 1n) en fonctionnement, sur la base de la différence de pression (Pw) détectée par chacune des secondes sections de détection de pression différentielle (90) et d'une caractéristique de résistance d'échangeur de chaleur de chacune des unités source de chaleur (1a, 1b, ..., 1n).
  8. Appareil source de chaleur selon la revendication 1, caractérisé en ce que :
    la section de détection de débit (5) détecte une quantité totale du fluide caloporteur qui s'écoule dans une pluralité d'unités (3a, 3b, ..., 3n) connectées en parallèle les unes aux autres par une conduite sur le côté charge ; et
    la première vanne de réglage de débit (4a) est une pluralité de premières vannes de réglage de débit (4a, 4b, ..., 4n), la pluralité de premières vannes de réglage de débit (4a, 4b, ..., 4n) règlent la quantité du fluide caloporteur qui s'écoule dans la pluralité d'unités (3a, 3b, ..., 3n) individuellement par des changements de leurs degrés d'ouverture.
  9. Appareil source de chaleur selon la revendication 8, caractérisé en ce que la première section de détection (11) est configurée pour :
    fermer complètement la seconde vanne de réglage de débit (7) lors d'une opération de test de l'appareil source de chaleur, ouvrir complètement seulement l'une des premières vannes de réglage de débit (4a, 4b, ..., 4n) correspondant à une unité ayant la plus grande résistance de conduite de la pluralité d'unités (3a, 3b, ..., 3n) et fermer complètement les une ou plusieurs autres premières vannes de réglage de débit (4a, 4b, ..., 4n), actionner les pompes (80) des unités source de chaleur respectives (1a, 1b, ..., 1n) à leur puissance nominale dans cet état, et stocker un point correspondant d'une valeur (Qn) du débit (Qt) détecté par la section de détection de débit (5) et une valeur (Pn) de la différence de pression (P) détectée par la première section de détection de pression différentielle (8) à cet instant en tant que premier point caractéristique (Sn) ;
    avoir la totalité des premières vannes de réglage de débit (4a, 4b, ..., 4n) ouvertes par la suite tout en ayant la seconde vanne de réglage de débit (7) complètement fermée, actionner les pompes (80) des unités source de chaleur respectives (1a, 1b, ..., 1n) à leur puissance nominale dans cet état, et stocker un point correspondant d'une valeur (Qm) du débit (Qt) détecté par la section de détection de débit (5) et une valeur (Pm) de la différence de pression (P) détectée par la première section de détection de pression différentielle (8) à cet instant en tant que second point caractéristique (Sm) ; et
    détecter une courbe d'approximation quadratique qui représente approximativement une relation entre une quantité d'eau (Q) qui s'écoule vers le côté charge et une différence (P) entre des pressions d'eau aux deux extrémités de la conduite de dérivation (6) en reliant le premier point caractéristique (Sn) et le second point caractéristique (Sm) stockés en tant que caractéristique de résistance de conduite côté charge.
EP15751873.9A 2014-02-20 2015-02-19 Dispositif source de chaleur Active EP3115707B1 (fr)

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EP3115707A1 (fr) 2017-01-11
CN105940272A (zh) 2016-09-14
KR20160096691A (ko) 2016-08-16
JPWO2015125863A1 (ja) 2017-03-30
EP3115707A4 (fr) 2017-12-13
CN105940272B (zh) 2019-03-08
JP6134856B2 (ja) 2017-05-24
WO2015125863A1 (fr) 2015-08-27
KR101805334B1 (ko) 2017-12-05

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