EP2320158B1 - Heat pump system - Google Patents

Heat pump system Download PDF

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Publication number
EP2320158B1
EP2320158B1 EP09802833.5A EP09802833A EP2320158B1 EP 2320158 B1 EP2320158 B1 EP 2320158B1 EP 09802833 A EP09802833 A EP 09802833A EP 2320158 B1 EP2320158 B1 EP 2320158B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
cycle
heat
heat source
secondary refrigerant
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.)
Not-in-force
Application number
EP09802833.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2320158A4 (en
EP2320158A1 (en
Inventor
Kuniaki Kawamura
Toshikazu SABUSAWA
Shinjiro Akaboshi
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.)
Mayekawa Manufacturing Co
Original Assignee
Mayekawa Manufacturing Co
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 Mayekawa Manufacturing Co filed Critical Mayekawa Manufacturing Co
Publication of EP2320158A1 publication Critical patent/EP2320158A1/en
Publication of EP2320158A4 publication Critical patent/EP2320158A4/en
Application granted granted Critical
Publication of EP2320158B1 publication Critical patent/EP2320158B1/en
Not-in-force 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • 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
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the present invention relates to a multistage heat pump system using NH 3 cooling medium (heat carrier) as a refrigerant at least on a certain lower stage side of the multistage heat pump system.
  • NH 3 cooling medium heat carrier
  • a series of heat cycles is formed. Each heat cycle corresponds to a stage of the system.
  • the stages are called the higher stage (higher temperature side) and the lower stage (lower temperature side); thus, in a multistage cooling/heating system, a sequence structure is defined.
  • the sequence structure is defined also in a case where the number of the stages is more than two.
  • a heat cycle of a higher stage is connected to the heat cycle of the adjacent lower stage via a cascade connection (i.e. a cascade condenser as a heat exchanger).
  • a certain heat cycle comprises a compressor that compresses and feeds the refrigerant (heat carrier) of the heat cycle.
  • the load on the environment can be reduced and a high degree of safety can be achieved.
  • to cool the objective space or material means to absorb the heat to be cooled (i.e. to absorb the heat corresponding to the objective heat load or the cooling demand load).
  • the heat carrier NH 3 in the higher stage is prevented from entering the heat carrier CO 2 in the lower stage, thanks to the adoption of the indirect cooling approach by use of the a relay heat exchanger (the cascade condenser).
  • the pressure of the CO 2 refrigerant in the temperature range of the heat exchange process of the CO 2 refrigerant cycle is higher than the pressure of the general refrigerant in the temperature range of a heat exchange process of the general refrigerant cycle; accordingly, if the general refrigerant in existing refrigerant facility is planned to be exchanged into CO 2 refrigerant, it is needed that the existing piping system corresponding to the existing refrigerant be replaced by a newly build piping system corresponding to CO 2 refrigerant. Thus, in this situation, the renewal work is not easily promoted because of high expenditure as to equipment replacement, even though the natural refrigerant such as CO 2 is socially desired, in view of environment load reduction.
  • CO 2 refrigerant instead of a conventional refrigerant used in the existing facility, there may be a case where the CO 2 refrigerant causes a cooling capacity shortage in dealing with a large cooling capacity (refrigeration load).
  • the refrigeration device adopts a liquid pump approach or a direct expansion approach (system) in a stage of the multi-stage system; and, it is unavoidable that there remains a very small amount of refrigerator oil in the NH 3 refrigerant.
  • the very small amount of refrigerator oil included in the NH 3 refrigerant remains in the evaporator, the oil causing performance degradation due to aging deterioration.
  • the control of the oil becomes a prerequisite matter in order to evade the performance degradation. And, the oil control accompanies complicated procedures or troublesome maintenance work.
  • the present invention aims at providing a heat pump system; whereby, a superior level of safety can be offered; high heat-transfer efficiency can be achieved; the existing facility can be effectively made use of; the lubricating oil for the system can be easily maintained and managed; the amount of the refrigerant can be restrained to a minimal level.
  • a heat pump system according to the preamble of independent claim 1 is known from JP2005-030622 .
  • the refrigerant NH 3 has the properties superior to those of the other general refrigerants.
  • the evaporative latent heat of the refrigerant NH 3 is higher than that of other general refrigerant.
  • the power consumption required for circulating the refrigerant NH 3 can be smaller than that required for circulating other brine refrigerants; thus, the performance of the cycle using the refrigerant NH 3 can be enhanced.
  • the secondary NH 3 refrigerant circulated in the secondary NH 3 refrigerant cycle absorbs the objective heat load (or absorbs the refrigeration load through the evaporator), by the head difference part or by both the head difference part and the circulating pump; in addition, the line system of the NH 3 refrigerant in the heat source cycle and the line system of the NH 3 refrigerant in the secondary NH 3 refrigerant cycle are completely separated from each other by the cascade condenser between the NH 3 heat source cycle and the secondary NH 3 refrigerant cycle; thus, the lubricating oil associated with the compressor in the NH 3 heat source cycle can be prevented from entering the secondary NH 3 refrigerant cycle. Accordingly, the maintenance work in relation to the lubricating oil can be confined within the machine room (the NH 3 heat source cycle), and the safety of the heat pump system can be ensured with simple maintenance.
  • the cascade condenser separates the secondary NH 3 refrigerant cycle from the NH 3 heat source cycle; and the NH 3 refrigerant in a clean condition is used in the secondary NH 3 refrigerant cycle, being free from contamination and aged deterioration; thus, the efficiency of the evaporator can be kept high.
  • the cascade condenser completely separates the line system of the secondary NH 3 refrigerant cycle from the line system of the NH 3 heat source cycle; thus, the amount of the refrigerant in the secondary NH 3 refrigerant cycle can be pertinently established in response to the objective heat load (the cooling demand load) to be cooled; accordingly, the amount of the refrigerant in the secondary NH 3 refrigerant cycle can be restrained to a minimum level.
  • the heat pump system whereby the secondary NH 3 refrigerant cycle that is indirectly connected to the heat source cycle via a second secondary refrigerant cycle.
  • the second secondary refrigerant cycle is provided between the heat source cycle and the secondary NH 3 refrigerant cycle.
  • the existing liquid pump approach or a direct expansion system can be used as a configuration of the heat source cycle; further, the secondary NH 3 refrigerant cycle that absorbs the objective load can be additionally provided.
  • the components of the existing facility can be made best use of.
  • Fig. 1 shows a configuration example not part of the claimed invention regarding the heat pump system in which a heat source cycle using NH 3 refrigerant and a secondary NH 3 refrigerant cycle using NH 3 refrigerant are combined.
  • the symbol A denotes a heat source cycle using NH 3 refrigerant as the heat source
  • the symbol B denotes a secondary NH 3 refrigerant cycle using NH 3 refrigerant, the secondary NH 3 refrigerant cycle including an evaporator 8 that generates an output (an absorption heat amount) corresponding to the objective heat load (the cooling demand load) to be cooled.
  • the heat source cycle A and the secondary NH 3 refrigerant cycle B are connected to each other so as to perform heat transfer via a cascade condenser 4; namely, the heat source cycle A and the secondary NH 3 refrigerant cycle B are directly connected to each other via the cascade condenser 4.
  • the heat source cycle A comprises a compressor 1, a condenser 2, an expansion means 3 (an expansion valve, a capillary tube, etc.), and a cascade condenser 4; thereby, the cascade condenser 4 functions as an evaporator in the heat source cycle A.
  • the heat source cycle A comprises the compression process, the condensation process, the expansion process, and the evaporation process regarding the NH 3 refrigerant cycle; thereby, the heat source cycle A absorbs heat from the secondary NH 3 refrigerant cycle B, via the cascade condenser 4.
  • the secondary NH 3 refrigerant cycle B comprises the cascade condenser 4 and an evaporator 8; thereby, the cascade condenser 4 functions as a heat absorbing device in the cycle B, and the evaporator 8 functions as a cooling device that absorbs the heat corresponding to the cooling demand load.
  • a head (liquid head) difference part H and a circulating pump 6 are provided between the evaporator 8 and the heat absorbing part (namely, the cascade condenser 4 in the example of Fig. 1 ) on the upstream side of the evaporator, in the cycle B.
  • a by-pass conduit line is provided in the cycle B so as to bypass the circulating pump 6; a flow rate control valve 5 is provided on the by-pass conduit line so as to be placed parallel to the circulating pump 6.
  • the flow rate control valve 5 the NH 3 refrigerant in the secondary NH 3 refrigerant cycle B can be circulated only with the liquid head of the head difference part H; or, the NH 3 refrigerant in the cycle B can be circulated with both the liquid head and the head of the pump 6.
  • it can be chosen whether the liquid in the cycle B can be circulated by only the liquid head H or by both the liquid head and the pump head.
  • a flow rate control valve 7 is arranged on the downstream side of the circulating pump 6 as well as the flow rate control valve 5.
  • the flow rate control valves 5 and 7 are controlled either manually or automatically; thereby, the opening of each valve 5 or 7 is regulated so that the flow rate of the NH 3 refrigerant streaming into the evaporator 8 is maintained within an appropriate range; in addition, the flow rate may be measured by a flow meter or estimated on the basis of the temperatures of the NH 3 refrigerant at the inlet and the outlet of the evaporator 8.
  • the heat source cycle A may be configured according to a NH 3 liquid pump approach or a NH 3 direct expansion system; thereby, the heat source cycle (to be modernized) can be configured with the existing liquid pump system or the existing NH 3 direct expansion system; further, the secondary NH 3 refrigerant cycle that absorbs the objective load can be additionally provided.
  • the components of the existing facility can be made best use of.
  • Fig. 2 shows a heat pump according to the invention in which a second secondary refrigerant cycle is arranged between the heat source cycle using NH 3 refrigerant and the secondary NH 3 refrigerant cycle using NH 3 refrigerant; hereby, the configurations of the heat source cycle and the secondary NH 3 refrigerant cycle are the same as those in Fig. 1 ; and the second secondary refrigerant used in the second secondary refrigerant cycle C may be, for instance, NH 3 and CO 2 .
  • the symbol A denotes the heat source cycle (of Fig. 2 ) using NH 3 refrigerant as the heat carrier in the heat source cycle, as is the case with the heat source cycle A in Fig. 1 ;
  • the symbol B denotes a secondary NH 3 refrigerant cycle (of Fig. 2 ) using NH 3 refrigerant;
  • the secondary NH 3 refrigerant cycle is connected to the heat source cycle A (of Fig. 2 ) via the second secondary refrigerant cycle C.
  • the heat of second secondary refrigerant cycle C is absorbed in (transferred to) the heat source cycle A via the cascade condenser 4 thereof; the second secondary refrigerant circulates in the second secondary refrigerant cycle C that comprises: the cascade condenser 4 that functions as the heat absorbing device which absorbs heat from the cycle C and transfers the heat to the cycle A; and, a cascade condenser 9 (an evaporator) that functions as a cooling heat supplying device which absorbs heat from the cycle B and transfers the heat to the cycle C.
  • the refrigerant to be circulated in the second secondary refrigerant cycle C is a natural refrigerant.
  • NH 3 is preferably used.
  • a head (liquid head) difference part H and a circulating pump 10 are provided between the cascade condenser (an evaporator) 9 and the heat absorbing part (namely, the cascade condenser 4 in the example of Fig. 2 ) on the upstream side of the cascade condenser 4, in the cycle B.
  • a by-pass conduit line is provided in the second secondary refrigerant cycle C so as to bypass the circulating pump 10; a flow rate control valve 11 is provided on the by-pass conduit line so as to be placed parallel to the circulating pump 10.
  • a flow rate control valve 12 is arranged on the downstream side of the circulating pump 10 as well as the flow rate control valve 11, a flow rate control valve 12 is arranged; by controlling the opening of the flow rate control valve 12, the flow rate regarding the second secondary refrigerant streaming into the cascade condenser (the evaporator) 9 is controlled so that the second secondary refrigerant circulates in the second secondary refrigerant cycle C, with a necessary flow rate in response to the required refrigeration load.
  • the refrigerant cycle that supplies refrigeration heat to (or absorbs the refrigeration load from) the secondary NH 3 refrigerant cycle B is diversified into multi-stages (i.e. the cycles A and C); thus, the heat pump system as described can easily optimize the amount of refrigerants in contrast to the lumped (single) stage approach. Accordingly, the saving (or minimization) of the refrigerants can be further promoted.
  • the refrigerant NH 3 has the properties superior to those of the other general refrigerants; for instance, the evaporative latent heat of the refrigerant NH 3 is higher than that of other general refrigerant.
  • the refrigerant NH 3 is applied to the heat source cycle A and the secondary NH 3 refrigerant cycle B; therefore, the power consumption required for circulating the refrigerant NH 3 can be smaller than that required for circulating other brine refrigerant; thus, the performance of the cycle using the refrigerant NH 3 can be enhanced.
  • the secondary NH 3 refrigerant is circulated in the secondary NH 3 refrigerant cycle B absorbs the objective heat load (or absorbs the refrigeration load through the evaporator 8), by the head difference part H or by both the head difference part H and the circulating pump 6; in addition, the line system of the NH 3 refrigerant in the cycle A and the line system of the NH 3 refrigerant in the cycle B are completely separated from each other by the cascade condenser 4 (as well as the cascade condenser 9) between the NH 3 heat source cycle A and the secondary NH 3 refrigerant cycle B; thus, the lubricating oil associated with the compressor 1 in the NH 3 heat source cycle A can be prevented from entering the secondary NH 3 refrigerant cycle B. Accordingly, the maintenance work in relation to the lubricating oil can be confined within the machine room (the NH 3 heat source cycle A), and the safety of the heat pump system can be ensured with simple maintenance.
  • the cascade condenser 4 (as well as the cascade condenser 9) separates the secondary NH 3 refrigerant cycle B from the NH 3 heat source cycle A; and the NH 3 refrigerant in a clean condition can be used in the cycle B, being free from contamination and aged deterioration; thus, the efficiency of the evaporator 8 can be kept high.
  • the cascade condenser 4 (as well as the cascade condenser 9) completely separates the line system of the secondary NH 3 refrigerant cycle B from the line system of the NH 3 heat source cycle A; thus, the amount of the refrigerant in the secondary NH 3 refrigerant cycle B can be pertinently established in response to the objective heat load (the cooling demand load) to be cooled; accordingly, the amount of the refrigerant in the secondary NH 3 refrigerant cycle B can be restrained to a minimum level.
  • the NH 3 heat source cycle A and the secondary NH 3 refrigerant cycle B may be connected via a pair (a series pair) of second secondary refrigerant cycles in two stage, although the NH 3 heat source cycle A and the secondary NH 3 refrigerant cycle B in Fig. 2 are connected via the second secondary refrigerant cycle C that itself forms a single stage.
  • the flow rate control valves 5 and 11 as well as the circulating pumps 6 and 10 are arranged on the downstream side of the cascade condensers 4 and 9, respectively; thereby, no special apparatus other than pipes are placed between the cascade condenser and the flow rate control valve (or the circulating pump).
  • a liquid refrigerant reservoir may be provided just on the down stream side of the cascade condenser 4 or 9. In this way, a stable liquid level regarding the refrigerant is ensured so that the liquid head of the head difference part H can be accurately controlled.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Other Air-Conditioning Systems (AREA)
EP09802833.5A 2008-07-28 2009-07-08 Heat pump system Not-in-force EP2320158B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US8406508P 2008-07-28 2008-07-28
PCT/JP2009/062469 WO2010013590A1 (ja) 2008-07-28 2009-07-08 ヒートポンプシステム

Publications (3)

Publication Number Publication Date
EP2320158A1 EP2320158A1 (en) 2011-05-11
EP2320158A4 EP2320158A4 (en) 2014-05-07
EP2320158B1 true EP2320158B1 (en) 2017-11-15

Family

ID=41610289

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09802833.5A Not-in-force EP2320158B1 (en) 2008-07-28 2009-07-08 Heat pump system

Country Status (4)

Country Link
EP (1) EP2320158B1 (ja)
JP (1) JP5246891B2 (ja)
NO (1) NO2320158T3 (ja)
WO (1) WO2010013590A1 (ja)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012086089A1 (ja) 2010-12-24 2012-06-28 株式会社前川製作所 ヒートポンプ装置の運転制御方法及び装置
KR101327818B1 (ko) * 2011-12-16 2013-11-08 부경대학교 산학협력단 하이브리드형 캐스케이드 냉동장치
JP5905278B2 (ja) * 2012-01-31 2016-04-20 株式会社前川製作所 冷凍装置の監視システムおよび監視方法
JP6319902B2 (ja) * 2014-07-08 2018-05-09 株式会社前川製作所 アイスリンクの冷却設備及び冷却方法
EP3457050B1 (en) * 2016-05-10 2024-04-03 Mitsubishi Electric Corporation Heat pump system
CN112460863A (zh) * 2020-12-10 2021-03-09 珠海格力电器股份有限公司 一种冷水机组及其制冷控制方法和装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3348402B2 (ja) * 1991-08-02 2002-11-20 三機工業株式会社 冷暖房装置
JP4145742B2 (ja) * 2003-07-07 2008-09-03 株式会社前川製作所 アイスクリームフリーザ
JP2005140349A (ja) 2003-11-04 2005-06-02 Hachiyo Engneering Kk 潤滑油混入に起因する不具合を排除したヒートポンプシステム
KR100858991B1 (ko) * 2004-09-30 2008-09-18 마에카와 매뉴팩쳐링 캄파니 리미티드 암모니아/ｃｏ2 냉동 시스템
JP4473151B2 (ja) * 2005-02-01 2010-06-02 日新興業株式会社 冷凍装置

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
JPWO2010013590A1 (ja) 2012-01-12
EP2320158A4 (en) 2014-05-07
JP5246891B2 (ja) 2013-07-24
NO2320158T3 (ja) 2018-04-14
EP2320158A1 (en) 2011-05-11
WO2010013590A1 (ja) 2010-02-04

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