EP3115707B1 - Heat source device - Google Patents

Heat source device 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
Authority
EP
European Patent Office
Prior art keywords
heat
heat source
transfer medium
water
flow
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.)
Active
Application number
EP15751873.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3115707A4 (en
EP3115707A1 (en
Inventor
Yuuji Matsumoto
Seiji Tsukiyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toshiba Carrier Corp
Original Assignee
Toshiba Carrier Corp
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Filing date
Publication date
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Publication of EP3115707A1 publication Critical patent/EP3115707A1/en
Publication of EP3115707A4 publication Critical patent/EP3115707A4/en
Application granted granted Critical
Publication of EP3115707B1 publication Critical patent/EP3115707B1/en
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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)
EP15751873.9A 2014-02-20 2015-02-19 Heat source device Active EP3115707B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014030530 2014-02-20
PCT/JP2015/054612 WO2015125863A1 (ja) 2014-02-20 2015-02-19 熱源装置

Publications (3)

Publication Number Publication Date
EP3115707A1 EP3115707A1 (en) 2017-01-11
EP3115707A4 EP3115707A4 (en) 2017-12-13
EP3115707B1 true EP3115707B1 (en) 2019-05-22

Family

ID=53878362

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15751873.9A Active EP3115707B1 (en) 2014-02-20 2015-02-19 Heat source device

Country Status (5)

Country Link
EP (1) EP3115707B1 (zh)
JP (1) JP6134856B2 (zh)
KR (1) KR101805334B1 (zh)
CN (1) CN105940272B (zh)
WO (1) WO2015125863A1 (zh)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015190525A1 (ja) * 2014-06-10 2015-12-17 東芝キヤリア株式会社 熱源機および熱源装置
JP6151409B2 (ja) * 2015-10-06 2017-06-21 木村工機株式会社 ヒートポンプ式熱源装置
EP3367021B1 (en) * 2015-10-20 2022-02-23 Mitsubishi Electric Corporation Refrigeration cycle device
EP3467395A4 (en) * 2016-05-27 2019-12-25 Toshiba Carrier Corporation HEAT SOURCE SYSTEM AND CONTROL METHOD OF HEAT SOURCE SYSTEM
JP6925455B2 (ja) 2018-02-07 2021-08-25 三菱電機株式会社 空調システム及び空調制御方法
WO2019171486A1 (ja) * 2018-03-07 2019-09-12 三菱電機株式会社 熱源装置および冷凍サイクル装置
DK3569935T3 (da) * 2018-05-17 2020-12-07 E On Sverige Ab Reversibelt varmepumpeaggregat og fjernvarmeenergidistributionssystem omfattende et sådan reversibelt varmepumpeaggregat
WO2020012750A1 (ja) * 2018-07-09 2020-01-16 東芝キヤリア株式会社 熱源システム、熱源機、制御装置
CN111795480B (zh) * 2019-04-08 2023-08-22 开利公司 热循环***和用于热循环***的控制方法
JP7286523B2 (ja) * 2019-12-10 2023-06-05 株式会社荏原製作所 給水装置、制御装置及びインバータ
JP7502728B2 (ja) 2020-03-23 2024-06-19 日本キヤリア株式会社 熱源システム

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6006528A (en) * 1996-10-31 1999-12-28 Sanyo Electric Co., Ltd. Air conditioning system
JP4939171B2 (ja) * 2006-10-30 2012-05-23 三菱重工業株式会社 熱源機および熱源システム
JP4829818B2 (ja) 2007-03-15 2011-12-07 新日本空調株式会社 １ポンプ方式熱源設備の運転制御方法
JP2009030821A (ja) * 2007-07-24 2009-02-12 Yamatake Corp 送水制御システムおよび送水制御方法
KR101244536B1 (ko) * 2009-02-13 2013-03-18 도시바 캐리어 가부시키가이샤 2차 펌프 방식 열원 시스템 및 2차 펌프 방식 열원 제어 방법
JP5320128B2 (ja) * 2009-03-31 2013-10-23 アズビル株式会社 送水温度制御装置および方法
JP2010270970A (ja) * 2009-05-21 2010-12-02 Mitsubishi Heavy Ind Ltd 熱源システム及びその制御方法並びにプログラム
JP5240134B2 (ja) 2009-09-07 2013-07-17 日立電線株式会社 冷水循環システム
US9157650B2 (en) * 2010-10-15 2015-10-13 Toshiba Carrier Corporation Heat source apparatus
JP5558400B2 (ja) * 2011-03-30 2014-07-23 三菱重工業株式会社 熱源システム及び熱源システムの台数制御方法
JP5787792B2 (ja) 2012-02-29 2015-09-30 三菱重工業株式会社 熱源システムの台数制御装置及びその方法並びに熱源システム

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

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

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