EP1873466A2 - Kältekreislauf und Wassererwärmer - Google Patents

Kältekreislauf und Wassererwärmer Download PDF

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Publication number
EP1873466A2
EP1873466A2 EP07252602A EP07252602A EP1873466A2 EP 1873466 A2 EP1873466 A2 EP 1873466A2 EP 07252602 A EP07252602 A EP 07252602A EP 07252602 A EP07252602 A EP 07252602A EP 1873466 A2 EP1873466 A2 EP 1873466A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
internal heat
pressure
refrigeration cycle
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.)
Withdrawn
Application number
EP07252602A
Other languages
English (en)
French (fr)
Other versions
EP1873466A3 (de
Inventor
Kenji c/o Hitachi Appliances Inc. Matsumura
Atsuhiko c/o Hitachi Appliances Inc. Yokozeki
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.)
Hitachi Global Life Solutions Inc
Original Assignee
Hitachi Appliances Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi Appliances Inc filed Critical Hitachi Appliances Inc
Publication of EP1873466A2 publication Critical patent/EP1873466A2/de
Publication of EP1873466A3 publication Critical patent/EP1873466A3/de
Withdrawn legal-status Critical Current

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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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2600/00—Control issues
    • F25B2600/05—Refrigerant levels
    • 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
    • F25B2600/00—Control issues
    • F25B2600/17—Control issues by controlling the pressure of the condenser
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures

Definitions

  • the present invention relates to improvement in reliability and performance of a refrigeration cycle and a water heater.
  • a refrigeration cycle using a natural refrigerant such as a CO2 refrigerant, of which ozone depletion potential is zero and of which global warming potential is much smaller as compared with chlorofluorocarbons attracts attention in recent years.
  • the CO2 refrigerant is characterized by constituting a trans-critical cycle in which a high pressure part exceeds a critical pressure, the pressure is defined by the temperature of a medium which exchanges heat with a gas cooler and by the refrigerant amount in the cycle, and particularly, it has the characteristic that the influence of the refrigerant amount is large as compared with a chlorofluorocarbon refrigerant. It is schematically shown in Fig. 4.
  • a preferred aim of the present invention is to provide a refrigeration cycle with high reliability, which can regulate the high pressure of the discharge pressure without using a tank for regulating a refrigerant.
  • a refrigeration cycle in which a compressor, a condenser, a variable pressure reducer and an evaporator are connected in sequence via a refrigerant pipe is configured to include an internal heat exchanger which causes a refrigerant which exits from the condenser and a refrigerant which is sucked into the compressor to exchange heat with each other, to detect the pressure of the refrigerant discharged from the compressor, and to change the refrigerant amount stored in the evaporator by regulating the pressure reduction amount of the variable pressure reducer in accordance with the detected pressure of the refrigerant.
  • a switching mechanism which switches the refrigerant exiting from the condenser to a passage which does not pass through the internal heat exchanger.
  • the internal heat exchanger is connected to a check valve, and that the direction of the refrigerant flowing in the internal heat exchanger at the time of cooling is the same direction as the direction of the refrigerant flowing in the internal heat exchanger at the time of heating.
  • the refrigerant is a CO2 refrigerant.
  • Fig. 1 is a block diagram showing a refrigeration cycle of a first embodiment.
  • a refrigerant is CO2, and the arrows of the solid line in the drawing show the flow of the refrigerant at the time of cooling.
  • the high-temperature and highpressure refrigerant from a compressor 10 passes through a four-way valve 20, emit heat to air at an outdoor heat exchanger 30 which works as a gas cooler by a-blower 50, passes through a variable pressure reducer 40 which is reduced in pressure reduction amount to the limit, and is further cooled at an internal heat exchanger 60.
  • the refrigerant passes through a stop valve 70a and a connection pipe 80a, is decreased in pressure by a variable pressure reducer 90, and deprives air of heat at an indoor heat exchanger 100 which works as an evaporator by a blower 110. Then, the refrigerant passes through a connection pipe 80b and a stop valve 70b, passes the four-way valve 20 again, is heated in the internal heat exchanger 60, and is sucked into the compressor 10 again.
  • the p-h diagram of this refrigeration cycle is as shown by the solid line in Fig. 2.
  • the characters A to F in the diagram designate the same positions in Fig. 1, and the heat exchanges of C to D and F to A are established in the internal heat exchanger.
  • the refrigeration cycle is as shown by the broken line in the diagram.
  • the evaporator changes from a point E in the vicinity of a quality of 0.2 to a point F in the vicinity of a quality of 1.0.
  • the diagram in which the pressure reduction amount of the variable pressure reducer 90 is decreased in this refrigeration cycle is shown in Fig. 3.
  • the pressure reduction amount By reducing the pressure reduction amount, the superheat amount of the compressor 10 can be reduced, and its heat exchange amount increases at the same time because the low temperature side of the internal heat exchanger 60 fully becomes low to be a saturation temperature. In this case, the evaporator changes from the quality in the vicinity of 0.1 to the quality in the vicinity of 0.65.
  • Fig. 5 shows the general relation between the quality and the void fraction in the saturation region at the low pressure side
  • Fig. 6 shows the relation between the quality and the refrigerant retained amount per evaporator unit volume in view of the void fraction.
  • the evaporator in Fig. 2 changes in quality from 0.2 to 1.0, and therefore, when averaging through the entire region, the refrigerant retained amount per evaporator unit volume is 350 kg/m3.
  • the quality is from 0.1 to 0.65, and therefore, the refrigerant retained amount per evaporator unit volume is 460 kg/m3.
  • the pressure reduction amount of the variable pressure reducer 90 is decreased to the limit, and the pressure reduction is performed by the variable pressure reducer 40.
  • the pressure reduction amount is lowered (by making the opening degree large) to be regulated to obtain the target pressure.
  • the control to increase the discharge pressure is performed by increasing the pressure reduction amount (by making the opening degree small).
  • the discharge pressure rises to a predetermined pressure or higher, the method of performing control to increase the pressure reduction amount or the like is conceivable.
  • Fig. 7 shows a second embodiment.
  • the reference numerals and characters in the drawing are substantially the same as the first embodiment, but on-off valves 130a and 130b are added so that the internal heat exchanger 60 can be bypassed.
  • the refrigeration cycle is the same as that of the first embodiment.
  • the on-off valve 130a is closed and the on-off valve 130b is opened, the refrigeration cycle is in the state of the broken line of the p-h diagram in Fig. 3. In this case, the quality of the evaporator changes from 0.45 to 1.0, and the refrigerant retained amount per unit volume becomes 300 kg/m3.
  • Fig. 8 shows a block diagram of a refrigeration cycle of a third embodiment.
  • the reference numerals and characters in the diagram are substantially the same as the first embodiment, but four of the check valves 120 are added.
  • the internal heat exchanger 60 is a parallel flow type internal heat exchanger, the heat exchange amount reduces, but in this embodiment, the internal heat exchanger is of a counter flow type at the time of cooling as well as heating, so that the configuration is possible only by one pressure reducer.
  • the configuration including the circuit bypassing the gas cooler 60 can be enabled by using the on-off valves or the variable pressure reducers as in the second embodiment.
  • Fig. 9 is a fourth embodiment.
  • the fourth embodiment is basically the same as the first embodiment, but a gas cooler 200 is configured to exchange heat with water, and is in the case of being used for a heat pump type water heater which flows low-temperature feed water 220a by a pump 210 to obtain high-temperature tapping 220b. If the temperature of the feed water 220a is high, the discharge pressure also rises in this case, and therefore, by moving the refrigerant to the evaporator 30 by regulating the variable pressure reducer 40, the discharge pressure can be regulated to a proper discharge pressure.
  • the refrigerant is CO2, but can be also applied to a chlorofluorocarbon refrigerant and an HC refrigerant which operate at a critical point pressure or less.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP07252602A 2006-06-28 2007-06-27 Kältekreislauf und Wassererwärmer Withdrawn EP1873466A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006177463A JP2008008523A (ja) 2006-06-28 2006-06-28 冷凍サイクル及び温水器

Publications (2)

Publication Number Publication Date
EP1873466A2 true EP1873466A2 (de) 2008-01-02
EP1873466A3 EP1873466A3 (de) 2010-03-17

Family

ID=38694849

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07252602A Withdrawn EP1873466A3 (de) 2006-06-28 2007-06-27 Kältekreislauf und Wassererwärmer

Country Status (2)

Country Link
EP (1) EP1873466A3 (de)
JP (1) JP2008008523A (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101957062A (zh) * 2010-11-09 2011-01-26 吴秀华 内外吸热高效节能热水器
CN102155791A (zh) * 2011-05-17 2011-08-17 康颖 热回收、冷利用热泵节能热水器
CN102538361A (zh) * 2012-03-06 2012-07-04 吴秀华 制冷吸热热泵热水器及制冷吸热方法
CN103017409A (zh) * 2013-01-15 2013-04-03 吴秀华 节能高效制冷、制热一体机
WO2018215425A1 (en) * 2017-05-22 2018-11-29 Swep International Ab Refrigeration system
EP3779326A4 (de) * 2018-04-11 2021-04-07 Mitsubishi Electric Corporation Kältekreislaufvorrichtung
SE2050095A1 (en) * 2020-01-30 2021-07-31 Swep Int Ab A refrigeration system
EP4040077A1 (de) * 2021-02-09 2022-08-10 Trane International Inc. Umkehrbare wärmepumpe

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4740984B2 (ja) * 2008-06-19 2011-08-03 三菱電機株式会社 冷凍空調装置
JP5414638B2 (ja) * 2010-08-25 2014-02-12 日立アプライアンス株式会社 空気調和システム
JP5802514B2 (ja) * 2011-10-19 2015-10-28 日立アプライアンス株式会社 ヒートポンプ式給湯機
WO2016009516A1 (ja) * 2014-07-16 2016-01-21 三菱電機株式会社 冷凍空調装置
JP2017193212A (ja) * 2016-04-19 2017-10-26 株式会社ヴァレオジャパン 車両用空調装置及びそれを備える車両
JP7267063B2 (ja) * 2019-03-27 2023-05-01 三菱重工サーマルシステムズ株式会社 冷凍サイクル装置

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JP2004061061A (ja) * 2002-07-31 2004-02-26 Matsushita Electric Ind Co Ltd 冷凍サイクル装置およびその運転方法
KR101058252B1 (ko) * 2003-01-28 2011-08-22 한라공조주식회사 초임계 냉동 사이클을 이용한 차량용 공조장치
JP2005075102A (ja) * 2003-08-29 2005-03-24 Mitsubishi Heavy Ind Ltd 車両用空気調和装置
EP1512924A3 (de) * 2003-09-05 2011-01-26 LG Electronics, Inc. Klimaanlage mit Wärmeüberträger und Vorrichtung zur Kühlkreisschaltung
JP4731806B2 (ja) * 2003-12-01 2011-07-27 パナソニック株式会社 冷凍サイクル装置およびその制御方法
JP4269323B2 (ja) * 2004-03-29 2009-05-27 三菱電機株式会社 ヒートポンプ給湯機
JP4613526B2 (ja) * 2004-06-23 2011-01-19 株式会社デンソー 超臨界式ヒートポンプサイクル装置

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101957062A (zh) * 2010-11-09 2011-01-26 吴秀华 内外吸热高效节能热水器
CN101957062B (zh) * 2010-11-09 2012-10-10 吴秀华 内外吸热高效节能热水器
CN102155791A (zh) * 2011-05-17 2011-08-17 康颖 热回收、冷利用热泵节能热水器
CN102155791B (zh) * 2011-05-17 2013-05-29 康颖 热回收、冷利用热泵节能热水器
CN102538361A (zh) * 2012-03-06 2012-07-04 吴秀华 制冷吸热热泵热水器及制冷吸热方法
CN103017409A (zh) * 2013-01-15 2013-04-03 吴秀华 节能高效制冷、制热一体机
CN103017409B (zh) * 2013-01-15 2015-12-02 吴秀华 节能高效制冷、制热一体机
US11480367B2 (en) 2017-05-22 2022-10-25 Swep International Ab Refrigeration system
JP2020521100A (ja) * 2017-05-22 2020-07-16 スウェップ インターナショナル アクティエボラーグ 冷凍システム
JP7022445B2 (ja) 2017-05-22 2022-02-18 スウェップ インターナショナル アクティエボラーグ 冷凍システム
WO2018215425A1 (en) * 2017-05-22 2018-11-29 Swep International Ab Refrigeration system
EP3779326A4 (de) * 2018-04-11 2021-04-07 Mitsubishi Electric Corporation Kältekreislaufvorrichtung
SE2050095A1 (en) * 2020-01-30 2021-07-31 Swep Int Ab A refrigeration system
WO2021154149A1 (en) * 2020-01-30 2021-08-05 Swep International Ab A refrigeration system and method
CN114945781A (zh) * 2020-01-30 2022-08-26 舒瑞普国际股份公司 制冷系统和方法
SE547354C2 (en) * 2020-01-30 2025-07-15 Swep Int Ab A refrigeration system
CN114945781B (zh) * 2020-01-30 2025-08-08 舒瑞普国际股份公司 制冷系统和方法
EP4040077A1 (de) * 2021-02-09 2022-08-10 Trane International Inc. Umkehrbare wärmepumpe
US11953240B2 (en) 2021-02-09 2024-04-09 Trane International Inc. Reversible heat pump
US12313307B2 (en) 2021-02-09 2025-05-27 Trane International Inc. Reversible heat pump

Also Published As

Publication number Publication date
EP1873466A3 (de) 2010-03-17
JP2008008523A (ja) 2008-01-17

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