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EP2708833A1 - Système de réfrigération en cascade - Google Patents

Système de réfrigération en cascade Download PDF

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Publication number
EP2708833A1
EP2708833A1 EP13181585.4A EP13181585A EP2708833A1 EP 2708833 A1 EP2708833 A1 EP 2708833A1 EP 13181585 A EP13181585 A EP 13181585A EP 2708833 A1 EP2708833 A1 EP 2708833A1
Authority
EP
European Patent Office
Prior art keywords
temperature side
cascade
high temperature
low temperature
heat exchanger
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.)
Granted
Application number
EP13181585.4A
Other languages
German (de)
English (en)
Other versions
EP2708833B1 (fr
Inventor
Katsutoshi Umehara
Tatsuya Sugiyama
Koji Ito
Atsuki Aoyagi
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 Johnson Controls Air Conditioning 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 EP2708833A1 publication Critical patent/EP2708833A1/fr
Application granted granted Critical
Publication of EP2708833B1 publication Critical patent/EP2708833B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near a heat exchanger

Definitions

  • the present invention relates to a cascade refrigerating system having a low temperature side refrigerating cycle and a high temperature side refrigerating cycle.
  • Patent Literature 1 discloses a known cascade refrigerating system. More specifically, Patent Literature 1 discloses a starter device for a cascade refrigerating system provided with a low temperature side refrigerant line provided with low temperature side refrigerant piping having a low temperature side compressor, a cascade condenser, a low temperature side expansion valve and a low temperature side heat exchanger intervening thereon, and a high temperature side refrigerant line provided with high temperature side refrigerant piping having a high temperature side compressor, a condenser, a high temperature side expansion valve and a low temperature side heat exchanger, which exchanges heat with the cascade condenser, intervening thereon, wherein a controller which is equipped with a thermostat for detecting the temperature of the refrigerant flowing in a low pressure part of the high temperature side refrigerant piping, starts the high temperature side compressor at the time of starting operation, starts the low temperature side compressor when the detected temperature of the thermostat falls to or below a set temperature and, when the ref
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. Hei2(1990)-143056
  • the low pressure in the high temperature side refrigerating cycle may fall too low and, depending on the load level, the refrigerating cycle may prove poor in the rate of rise or inefficient.
  • the present invention is intended to restrain a fall in space heating capacity due to a deterioration in the rate of rise by suppressing losses at the time of rise of the refrigerating cycle in a cascade refrigerating system.
  • a low temperature side refrigerating cycle in which a low temperature side compressor, a cascade heat exchanger, a low temperature side expansion valve and a low temperature side heat exchanger (an evaporator) are connected by low temperature side refrigerant piping and a high temperature side refrigerating cycle in which a high temperature side compressor, a condenser for exchanging heat between high temperature side refrigerant and refrigerated medium, a high temperature side expansion valve and the cascade heat exchanger are connected by high temperature side refrigerant piping are thermally connected via the cascade heat exchanger, and/or the low temperature side compressor is started when the cascade refrigerating system is to be started, and subsequently the high temperature side compressor is started.
  • a low temperature side refrigerating cycle in which a low temperature side compressor, a cascade heat exchanger, a low temperature side expansion valve and a low temperature side heat exchanger (an evaporator) are connected by low temperature side refrigerant pimping and a high temperature side refrigerating cycle in which a high temperature side compressor, a condenser for exchanging heat between high temperature side refrigerant and refrigerated medium, a high temperature side expansion valve and the cascade heat exchanger are connected by high temperature side refrigerant piping are thermally connected via the cascade heat exchanger, the low temperature side compressor is started when the cascade refrigerating system is to be started, and subsequently the high temperature side compressor is started.
  • this embodiment which is a cascade refrigerating system in which the low temperature side refrigerating cycle and the high temperature side refrigerating cycle are thermally connected via the cascade heat exchanger
  • the high temperature side compressor is started after the low temperature side compressor is started and the temperature of the cascade heat exchanger is raised, with the result that the cascade cycle can be started in a state in which the temperature of the cascade heat exchanger is high, so that a stable cascade cyclic operation is possible without inviting a fall in the low pressure of the high temperature side refrigerating cycle, and accordingly it is possible to restrain a fall in space heating capacity due to a deterioration in the rate of rise of the cascade refrigerating system.
  • Fig. 1 is a configurational diagram of the refrigerating cycle when the cascade refrigerating system of this embodiment is in cascade heating operation.
  • the cascade refrigerating system is provided with a low temperature side refrigerating cycle 1 and a high temperature side refrigerating cycle 10.
  • the low temperature side refrigerating cycle 1 is configured by connecting a low temperature side compressor 2, an expansion valve 3, a low temperature side heat exchanger 4, a heat exchanger (a condenser) 20 and a cascade heat exchanger 21 by low temperature side refrigerating piping.
  • the high temperature side refrigerating cycle 10 is configured by connecting a high temperature side compressor 11, the heat exchanger 20, a high temperature side expansion valve 12 and the cascade heat exchanger 21 by high temperature side refrigerating piping. Refrigerated medium is caused to flow into the heat exchanger 20 by being circulated by a pump, and is heated by its heat exchange with refrigerant in the heat exchanger 20, and warm water thereby generated is supplied to where it is needed.
  • Fig. 2 is a control flow chart of the cascade refrigerating system of this embodiment. With reference to Fig. 2 , a control flow to start a cascade cycle from a state in which the cascade cycle of the cascade refrigerating system is at halt in cascade heating operation to supply high temperature water will be described below.
  • the refrigerant compressed by the low temperature side compressor 2 turns into high pressure gas and flows into the cascade heat exchanger 21, in which the high pressure gas refrigerant is condensed by exchanging heat with low pressure gas-liquid refrigerant of the high temperature side refrigerating cycle 10.
  • the condensed refrigerant is evaporated in the low temperature side heat exchanger 4 by exchanging heat with air taken in by a fan to become gasified.
  • This gas refrigerant is reduced in pressure by the expansion valve 3 to turn into gas-liquid flow refrigerant, sucked into the compressor 2 to be compressed into high pressure gas again.
  • this cyclic process is repeated.
  • the refrigerant compressed in the high temperature side compressor 11 turns into high pressure gas, which flows into the heat exchanger 20 and exchanges heat with the refrigerated medium 30 to become liquefied.
  • the liquid refrigerant is expanded by the expansion valve 12 under reduced pressure to turn into gas-liquid flow refrigerant and flows into the cascade heat exchanger 21, where it exchanges heat with gas refrigerant of the low temperature side refrigerating cycle 1 to become gasified.
  • This gas refrigerant is sucked into the compressor 11 to be compressed into high pressure gas again. In the high temperature side refrigerating cycle 10, this cyclic process is repeated.
  • the cascade refrigerating system is started (S1). If the temperature of the cascade heat exchanger 21 is low even though the low temperature side refrigerating cycle 1 is started, the pressure in the low temperature side refrigerating cycle 1 will fall. If the high temperature side refrigerating cycle 10 is started in a fallen state of the capacity of the low temperature side refrigerating cycle 1, the pressure in the low temperature side refrigerating cycle 1 will further fall, and the low pressure in the high temperature side refrigerating cycle 10 will also fall. This would mean a loss in calorific value at the time of rise, resulting in a cycle poor in .the rate of rise.
  • the high temperature side refrigerating cycle 10 is started in a state in which the low temperature side refrigerating cycle 1 is already started and the temperature of the cascade heat exchanger 21 is raised, a stable refrigerating cycle will be achieved without allowing the pressure in the high temperature side refrigerating cycle 10 to fall. Therefore, in order to start the low temperature side refrigerating cycle 1 to accomplish operation to raise the temperature of the cascade heat exchanger 21, first the low temperature side compressor 2 is started (S2). And when the temperature of the cascade heat exchanger 21 rises to a prescribed level (C°C) (S3), the high temperature side compressor 11 is started (S4). After that, usual cascade heating operation is performed (S5). By the cycle starting so far described, stable cycling operation is made possible at an improved rate of rise in cascade heating operation.
  • Fig. 3 is another control flow chart of the cascade refrigerating system of this embodiment.
  • the control charted in Fig. 2 can be replaced by that charted in Fig. 3 . More specifically, first the cascade refrigerating system is started (S1). Next, as in the case of Fig. 2 , the low temperature side compressor 2 is started (S2). And when the temperature of the cascade heat exchanger 21 has risen to the prescribed level (C°C) (S3-1), the high temperature side compressor 11 is started (S4).
  • any abnormality is detected in the low temperature side refrigerating cycle 1 or in the high temperature side refrigerating cycle 10 during cascade heating operation and the low temperature side compressor 2 or the high temperature side compressor 11 is stopped, the low temperature side compressor 2 and the high temperature side compressor 11 is stopped, followed by retrial of starting.
  • This retried starting can also be cascade heating operation similar to what was described with respect to the embodiment.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP13181585.4A 2012-09-14 2013-08-23 Système de réfrigération en cascade Active EP2708833B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2012202191A JP2014055753A (ja) 2012-09-14 2012-09-14 二元冷凍装置

Publications (2)

Publication Number Publication Date
EP2708833A1 true EP2708833A1 (fr) 2014-03-19
EP2708833B1 EP2708833B1 (fr) 2020-03-25

Family

ID=49033908

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13181585.4A Active EP2708833B1 (fr) 2012-09-14 2013-08-23 Système de réfrigération en cascade

Country Status (4)

Country Link
EP (1) EP2708833B1 (fr)
JP (1) JP2014055753A (fr)
CN (1) CN103673366B (fr)
ES (1) ES2781483T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104913435A (zh) * 2015-05-12 2015-09-16 珠海格力电器股份有限公司 空调系统、空调器及其控制方法
EP3073218A1 (fr) * 2015-03-11 2016-09-28 Heatcraft Refrigeration Products LLC Condenseur à microcanaux refroidi par eau
CN108266915A (zh) * 2018-03-05 2018-07-10 天津商业大学 一种使用单一工质co2作制冷剂的复叠制冷系统
CN109210817A (zh) * 2018-10-22 2019-01-15 重庆优玛泰思特仪器有限公司 三级复叠制冷系统
CN116951802A (zh) * 2023-08-17 2023-10-27 无锡暖芯半导体科技有限公司 一种节能的宽温段双机复叠低温机组蒸发器模组装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015183929A (ja) * 2014-03-24 2015-10-22 サンデンホールディングス株式会社 ヒートポンプ式暖房装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5170639A (en) * 1991-12-10 1992-12-15 Chander Datta Cascade refrigeration system
JP2004190917A (ja) * 2002-12-10 2004-07-08 Sanyo Electric Co Ltd 冷凍装置
WO2008150289A1 (fr) * 2007-06-04 2008-12-11 Carrier Corporation Système réfrigérant avec circuits en cascade et caractéristiques d'amélioration de performance

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JPS61101770A (ja) * 1984-10-23 1986-05-20 三菱電機株式会社 ヒ−トポンプ式冷暖房給湯機
JPH07104060B2 (ja) * 1988-11-24 1995-11-13 ダイキン工業株式会社 二元冷凍装置の起動装置
JPH03263556A (ja) * 1990-03-12 1991-11-25 Sanyo Electric Co Ltd 多元冷凍装置
JPH07104061B2 (ja) * 1990-11-30 1995-11-13 ダイキン工業株式会社 二元冷凍装置
JPH08189713A (ja) * 1995-01-13 1996-07-23 Daikin Ind Ltd 二元冷凍装置
JP2000065431A (ja) * 1998-08-24 2000-03-03 Matsushita Electric Ind Co Ltd 冷凍サイクル装置および冷凍サイクル装置用圧縮機
JP3175706B2 (ja) * 1998-09-30 2001-06-11 ダイキン工業株式会社 二元冷凍装置
US6766652B2 (en) * 2002-12-18 2004-07-27 Gsle Development Corporation Dual independent chamber ultra-low temperature freezer
JP2004286289A (ja) * 2003-03-20 2004-10-14 Sanyo Electric Co Ltd 冷媒サイクル装置
KR20050062077A (ko) * 2003-12-19 2005-06-23 엘지전자 주식회사 이원 냉동시스템
JP2006064199A (ja) * 2004-08-24 2006-03-09 Daikin Ind Ltd 冷凍装置
CN201021855Y (zh) * 2006-12-20 2008-02-13 广东西屋康达空调有限公司 复叠耦合式高温热回收空调机组
CN101809383A (zh) * 2008-02-04 2010-08-18 三菱电机株式会社 空调供热水复合系统
JP5711448B2 (ja) * 2009-02-24 2015-04-30 ダイキン工業株式会社 ヒートポンプシステム
CN102506502A (zh) * 2011-10-19 2012-06-20 广东美的暖通设备限公司 蓄热式复叠循环热水机及其控制方法

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5170639A (en) * 1991-12-10 1992-12-15 Chander Datta Cascade refrigeration system
JP2004190917A (ja) * 2002-12-10 2004-07-08 Sanyo Electric Co Ltd 冷凍装置
WO2008150289A1 (fr) * 2007-06-04 2008-12-11 Carrier Corporation Système réfrigérant avec circuits en cascade et caractéristiques d'amélioration de performance

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3073218A1 (fr) * 2015-03-11 2016-09-28 Heatcraft Refrigeration Products LLC Condenseur à microcanaux refroidi par eau
CN104913435A (zh) * 2015-05-12 2015-09-16 珠海格力电器股份有限公司 空调系统、空调器及其控制方法
CN104913435B (zh) * 2015-05-12 2022-01-18 珠海格力电器股份有限公司 空调系统、空调器及其控制方法
CN108266915A (zh) * 2018-03-05 2018-07-10 天津商业大学 一种使用单一工质co2作制冷剂的复叠制冷系统
CN109210817A (zh) * 2018-10-22 2019-01-15 重庆优玛泰思特仪器有限公司 三级复叠制冷系统
CN116951802A (zh) * 2023-08-17 2023-10-27 无锡暖芯半导体科技有限公司 一种节能的宽温段双机复叠低温机组蒸发器模组装置

Also Published As

Publication number Publication date
ES2781483T3 (es) 2020-09-02
CN103673366A (zh) 2014-03-26
EP2708833B1 (fr) 2020-03-25
CN103673366B (zh) 2016-08-10
JP2014055753A (ja) 2014-03-27

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