US20110094251A1 - Dual turbo centrifugal chiller - Google Patents

Dual turbo centrifugal chiller Download PDF

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Publication number
US20110094251A1
US20110094251A1 US12/796,014 US79601410A US2011094251A1 US 20110094251 A1 US20110094251 A1 US 20110094251A1 US 79601410 A US79601410 A US 79601410A US 2011094251 A1 US2011094251 A1 US 2011094251A1
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United States
Prior art keywords
compressor
evaporator
condenser
compressors
impellers
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.)
Abandoned
Application number
US12/796,014
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English (en)
Inventor
Kil Young Kim
Jin Sung Kim
Tae Jin Kang
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LG Electronics Inc
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Individual
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Filing date
Publication date
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Assigned to LS MTRON LTD. reassignment LS MTRON LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KANG, TAE JIN, KIM, JIN SUNG, KIM, KIL YOUNG
Publication of US20110094251A1 publication Critical patent/US20110094251A1/en
Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LS MTRON, LTD.
Abandoned 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • 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
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities

Definitions

  • This disclosure relates to a dual turbo centrifugal chiller, particularly to a dual turbo centrifugal chiller configured to decrease head of a compressor among components of two individual chillers, decrease the size of the chiller, and increase efficiency.
  • a general chiller includes a compressor, an evaporator, a condenser, and an expansion valve, and circulates a refrigerant to transfer heat from the evaporator to the condenser through heat exchange.
  • FIG. 1 is a diagram schematically illustrating a general chiller 10 .
  • the chiller 10 includes an evaporator 30 , a condenser 20 , and a compressor 40 .
  • Cold water 31 flows through the evaporator 30
  • cooling water 21 flow through the condenser 20 .
  • the compressor 40 in which a refrigerant 51 , 52 is circulated connects the evaporator 30 to the condenser 20 .
  • the refrigerant 51 that passes through the evaporator 30 flows into the compressor 40 through an inlet portion 47 of the compressor 40 , and the refrigerant 52 compressed by two-stage impellers 41 and 42 flows out of an outlet portion 48 of the compressor 40 and then flows into the condenser 20 .
  • the two-stage impellers 41 and 42 are provided on a shaft 43 , and the impellers 41 and 42 are rotated as the shaft 43 is rotated by a motor 45 .
  • gears 44 and 46 are provided to connect the motor 45 to the shaft 43 so as to transmit torque.
  • a thrust bearing may be connected between the gear 44 and the shaft 43 .
  • a load applied to the bearing increases because a thrust that is transferred to the gears 46 and 44 is focused in one direction, and, thus, a load applied to the motor 45 also increases.
  • a load applied to the motor 45 increases, an outlet temperature of the cold water increases, which results in an increase in head of the compressor. As a result, the efficiency of the compressor is decreased.
  • a ‘dual turbo centrifugal chiller’ which includes two chillers connected to each other has been used.
  • the dual turbo centrifugal chiller has an increased capacity by increasing the chilling efficiency of the chiller itself.
  • two compressors are provided.
  • one of the two compressors has a higher head than the other. Therefore, the two compressors have to be independently designed and manufactured. That is, a driving unit for driving an impeller of each of the compressors is additionally needed, and the entire size of the chiller is increased. Accordingly, as described above, there is a problem in that the efficiency of the compressor is decreased.
  • This disclosure provides a dual turbo centrifugal chiller in which two compressors, two evaporators, and two condensers are included to decrease heads of the compressors, the compressors are configured to operate with the same head, and impellers of the compressors are driven by a single driving unit, thereby achieving a decrease in size and an increase in efficiency.
  • a dual turbo centrifugal chiller including: first and second evaporators connected in series or in parallel; first and second condensers connected in series or in parallel; and first and second compressors including impellers, wherein cold water passes through the second evaporator after passing through the first evaporator, and cooling water passes through the second condenser after passing through the first condenser, the first compressor containing a refrigerant connects the first condenser to the second evaporator, and the second compressor containing a refrigerant connects the second condenser to the first evaporator, and the impellers of the first compressor and the second compressor are rotated simultaneously using a single driving unit.
  • impellers of the first and second compressors may be connected with a single rotation shaft, and the impellers of the first and second compressors may be rotated simultaneously as the rotation shaft is rotated using the driving unit.
  • the driving unit may be connected to the center of the rotation shaft, and the impellers of the first and second compressors may be opposed with the center of the rotation shaft between them.
  • inlet portions of the first and second compressors may be provided with inlet guide vanes (IGVs) respectively.
  • IGVs inlet guide vanes
  • first and second compressors may have different capacities from each other.
  • the dual turbo centrifugal chiller including the two evaporators, the two compressors and the two condensers maintains the reduced head of each compressor, it is possible to achieve the optimal performance of the compressor.
  • FIG. 1 is a diagram schematically illustrating a general chiller
  • FIG. 2 is a diagram schematically illustrating a dual turbo centrifugal chiller according to an embodiment
  • FIG. 3 is a diagram schematically illustrating a dual turbo centrifugal chiller according to another embodiment.
  • FIG. 2 is a diagram schematically illustrating a dual turbo centrifugal chiller 101 according to an embodiment.
  • a first evaporator 121 and a second evaporator 122 are connected in series.
  • Cold water 123 flows into an end of the first evaporator 121 connected in series, passes through the first evaporator 121 , passes through the second evaporator 122 , and then flows out.
  • a first condenser 111 and a second condenser 112 are connected in series. Cooling water 113 passes through the first condenser 111 , flows into the second condenser 112 , passes through the second condenser 112 , and then flows out.
  • a first compressor 131 is connected to the first condenser 111 and the second evaporator 122 such that a refrigerant of the first compressor 131 is circulated to exchange heat with the cooling water 113 of the first condenser 111 and the cold water 123 of the second evaporator 122 .
  • a second compressor 132 is connected to the second condenser 112 and the first evaporator 121 such that a refrigerant of the second compressor 132 is circulated to exchange heat with the cooling water 113 of the second compressor 112 and the cold water 123 of the first evaporator 121 .
  • a temperature of the cold water that flows into the first evaporator 121 is 12° C.
  • a temperature of the cold water that flows out of the second evaporator 122 is 7° C.
  • a temperature of the cooling water that flows into the first condenser 111 is 32° C.
  • a temperature of the cooling water that flows out of the second condenser 112 is 37° C.
  • a head of the first compressor 131 is 27.5° C. (34.5° C.-7° C.), and a head of the second compressor 132 is also 27.5° C. (37° C.-9.5° C.).
  • the heads of the two compressors 131 and 132 are equal to each other. Accordingly, as described below, a design for simultaneously driving impellers of the two compressors using a single driving unit may be easily achieved.
  • the first compressor 131 is a two-stage compression system having two impellers 145 and 146 .
  • a refrigerant 151 flows out of the second evaporator 122 into the first compressor 131 through an inlet portion 141 of the first compressor 131 , and the refrigerant is compressed while passing through the impellers 145 and 146 .
  • the compressed refrigerant 152 flows out of the first compressor 131 through an outlet portion 142 and flows into the first condenser 111 .
  • the second compressor 132 is a two-stage compression system having two impellers 143 and 144 .
  • a refrigerant 153 that flows out of the first evaporator 121 flows into the second compressor 132 through an inlet portion 143 of the second compressor 132 , and the refrigerant is compressed while passing through the impellers 143 and 144 .
  • the compressed refrigerant 154 flows out of the second compressor 132 through an outlet portion 144 and flows into the second condenser 122 .
  • a single driving unit 163 for rotating the impellers 143 , 144 , 145 , and 146 of the two compressors 131 and 132 is provided.
  • an electric motor is used as the driving unit 163 .
  • the impellers 143 , 144 , 145 , and 146 of the two compressors 131 and 132 are connected with a rotation shaft 161 .
  • a gear 162 is provided at the center of the rotation shaft 161 , the impellers 145 and 146 of the first compressor 131 and the impellers 143 and 144 of the second compressor 132 are opposed with the center of the rotation shaft 161 between them.
  • An end portion of the driving unit 163 is connected to a gear, and the gear connected to the driving unit 163 is engaged with a gear 162 of the rotation shaft 161 .
  • the single driving unit 163 rotates the rotation shaft 161 , and as the rotation shaft 161 is rotated, the impellers 143 , 144 , 145 , and 146 of the two compressors 131 and 132 are rotated simultaneously.
  • the two individual compressors 131 and 132 are driven by the single driving unit 163 , the entire volume of the compressor system is reduced. Therefore, the entire size of the dual turbo centrifugal chiller 101 is reduced.
  • the inlet portions of the first and second compressors 131 and 132 are provided with inlet guide vanes (IGVs) for adjusting loads applied thereto in order to facilitate load adjustment.
  • IGVs inlet guide vanes
  • the first and second compressors 131 and 132 are separated from each other, various combinations of capacity may be attained with the compressors and the heat exchangers (the condensers and the evaporators).
  • the capacities of the compressors 131 and 132 may be set to 1,000 RT and 500 RT, respectively.
  • the size of the heat exchanger is determined according to the capacity of the compressor. Even in this case, the impellers of the compressors are disposed symmetrically on the single rotation shaft, and since the impellers are disposed symmetrically, the thrust cancellation effect of the bearing is exhibited even in the case where the capacities of the two compressors are different from each other.
  • the two evaporators 121 and 122 are connected in series, and the two condensers 111 and 112 are connected in series, however, the embodiment is not limited to that configuration.
  • another embodiment will be described with reference to FIG. 3 .
  • FIG. 3 is a diagram schematically illustrating a dual turbo centrifugal chiller 201 according to another embodiment.
  • a first evaporator 221 and a second evaporator 222 are connected in parallel.
  • Cold water 223 flows into an end of the first evaporator 221 connected in parallel and flows out of the other end of the first evaporator 221 , flows into an end of the second evaporator 222 , passes through the second evaporator 222 , and flows out of the other end of the second evaporator 222 .
  • a first condenser 211 and a second condenser 212 are connected in parallel. Cooling water 213 flows into an end of the first condenser 211 connected in parallel, flows out of the other end of the first condenser 211 , flows into an end of the second condenser 212 , passes through the second condenser 212 , and flows out of the other end of the second condenser 212 .
  • a first compressor 231 is connected to the first condenser 211 and the second evaporator 222 , and a refrigerant of the first compressor 231 is circulated to exchange heat with the cooling water of the first condenser 211 and the cold water of the second evaporator 222 .
  • a second compressor 232 is connected to the second condenser 212 and the first evaporator 221 , and a refrigerant of the second compressor 232 is circulated to exchange heat with the cooling water of the second condenser 212 and the cold water of the first evaporator 221 .
  • a temperature of the cold water that flows into the first evaporator 221 is 12° C.
  • a temperature of the cold water that flows out of the second evaporator 222 is 7° C.
  • a temperature of the cooling water that flows into the first condenser 211 is 32° C.
  • a temperature of the cooling water that flows out of the second condenser 212 is 37° C.
  • a head of the first compressor 231 is 27.5° C. (34.5° C.-7° C.), and a head of the second compressor 232 is also 27.5° C. (37° C.-9.5° C.). That is, the heads of the two compressors are equal to each other.
  • connection relationships between impellers 245 , 246 , 247 , and 248 of the compressors 231 and 232 , the rotation shaft 161 , a gear 262 , and a driving unit 263 provided in the dual turbo centrifugal chiller 201 according to this embodiment, and a flow of a refrigerant 251 , 252 , 253 , and 254 at inlet and outlet portions 243 and 244 of the compressor are the same as those of the embodiment illustrated in FIG. 2 , a detailed description thereof will be omitted.
  • the two evaporators may be connected in serial or in parallel, and the two condensers may be connected in serial or in parallel.
  • cold water passes through a first evaporator and a second evaporator
  • cooling water passes through a second condenser after passing through a first condenser
  • a first compressor containing a refrigerant is connected to the first condenser and the second evaporator
  • a second compressor containing a refrigerant is connected to the second condenser and the first evaporator

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/796,014 2009-10-27 2010-06-08 Dual turbo centrifugal chiller Abandoned US20110094251A1 (en)

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KR1020090102209A KR101065549B1 (ko) 2009-10-27 2009-10-27 듀얼 터보 냉동기
KR10-2009-0102209 2009-10-27

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KR (1) KR101065549B1 (ko)
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103615842A (zh) * 2013-10-29 2014-03-05 广州市盈夏制冷技术有限公司 一种节能整体压缩机装置
WO2015089362A1 (en) * 2013-12-12 2015-06-18 Johnson Controls Technology Company Steam turbine driven centrifugal heat pump
US20230296243A1 (en) * 2021-06-16 2023-09-21 Colorado State University Research Foundation Air source heat pump system and method of use for industrial steam generation

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101372353B1 (ko) * 2011-12-21 2014-03-13 정방균 터보압축기를 이용한 열펌프시스템
KR102201745B1 (ko) * 2014-05-20 2021-01-12 엘지전자 주식회사 터보 칠러 및 이를 포함하는 칠러 시스템
CN104235988B (zh) * 2014-10-16 2017-02-01 珠海格力电器股份有限公司 采用水作为制冷剂的离心式空调机组及运行方法
EP3931503A1 (en) 2019-02-27 2022-01-05 Johnson Controls Tyco IP Holdings LLP Condenser arrangement for a chiller

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5845509A (en) * 1997-09-26 1998-12-08 Shaw; David N. Variable speed parallel centrifugal compressors for HVAC and refrigeration systems
US5875637A (en) * 1997-07-25 1999-03-02 York International Corporation Method and apparatus for applying dual centrifugal compressors to a refrigeration chiller unit
US5996356A (en) * 1996-10-24 1999-12-07 Mitsubishi Heavy Industries, Ltd. Parallel type refrigerator
US20030233838A1 (en) * 2002-06-19 2003-12-25 Lg Electronics Inc. Air conditioning system with two compressors and method for operating the same
US6772599B2 (en) * 2002-08-06 2004-08-10 York International Corporation Stability control system and method for compressors operating in parallel
US7240515B2 (en) * 2002-02-28 2007-07-10 Turbocor, Inc. Centrifugal compressor
WO2008045039A1 (en) * 2006-10-10 2008-04-17 Carrier Corporation Dual-circuit chiller with two-pass heat exchanger in a series counterflow arrangement

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE419128B (sv) 1974-09-05 1981-07-13 Projectus Ind Produkter Ab Forfarande for drift av vermepumpanleggning
JPS5926206Y2 (ja) 1979-12-22 1984-07-30 ダイキン工業株式会社 熱回収式タ−ボ冷凍機
JPH07120084A (ja) * 1993-10-27 1995-05-12 Ebara Corp ターボ冷凍機
JPH10131889A (ja) * 1996-10-25 1998-05-19 Mitsubishi Heavy Ind Ltd 冷凍機用圧縮機
KR100378531B1 (ko) 2001-04-11 2003-04-03 엘지전선 주식회사 터보냉동기의 냉매와 오일 분리/회수장치
CN1405457A (zh) * 2001-09-20 2003-03-26 成都希望电子研究所 离心式制冷压缩装置
JP2007177695A (ja) * 2005-12-28 2007-07-12 Ishikawajima Harima Heavy Ind Co Ltd ターボ圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5996356A (en) * 1996-10-24 1999-12-07 Mitsubishi Heavy Industries, Ltd. Parallel type refrigerator
US5875637A (en) * 1997-07-25 1999-03-02 York International Corporation Method and apparatus for applying dual centrifugal compressors to a refrigeration chiller unit
US5845509A (en) * 1997-09-26 1998-12-08 Shaw; David N. Variable speed parallel centrifugal compressors for HVAC and refrigeration systems
US7240515B2 (en) * 2002-02-28 2007-07-10 Turbocor, Inc. Centrifugal compressor
US20030233838A1 (en) * 2002-06-19 2003-12-25 Lg Electronics Inc. Air conditioning system with two compressors and method for operating the same
US6772599B2 (en) * 2002-08-06 2004-08-10 York International Corporation Stability control system and method for compressors operating in parallel
WO2008045039A1 (en) * 2006-10-10 2008-04-17 Carrier Corporation Dual-circuit chiller with two-pass heat exchanger in a series counterflow arrangement

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103615842A (zh) * 2013-10-29 2014-03-05 广州市盈夏制冷技术有限公司 一种节能整体压缩机装置
WO2015089362A1 (en) * 2013-12-12 2015-06-18 Johnson Controls Technology Company Steam turbine driven centrifugal heat pump
US10704810B2 (en) 2013-12-12 2020-07-07 Johnson Controls Technology Company Steam turbine driven centrifugal heat pump
US20230296243A1 (en) * 2021-06-16 2023-09-21 Colorado State University Research Foundation Air source heat pump system and method of use for industrial steam generation

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KR101065549B1 (ko) 2011-09-19
KR20110045574A (ko) 2011-05-04
CN102052796A (zh) 2011-05-11

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